CN114076146A

CN114076146A - Bearing, and rocking bearing device for reciprocating motion

Info

Publication number: CN114076146A
Application number: CN202110786478.1A
Authority: CN
Inventors: 徐学庆
Original assignee: Individual
Current assignee: Individual
Priority date: 2020-08-15
Filing date: 2020-08-15
Publication date: 2022-02-22
Also published as: CN114076145A; CN114076147A; CN112112894A; CN112112894B; CN115638186A

Abstract

A combined bearing and a rocking bearing device for reciprocating motion are provided with an outer bearing ring and an inner bearing ring having a center of sphere coaxial with the outer bearing ring, a plurality of rows of balls are arranged in at least two rows in the axial direction across the center of sphere in the radial direction, and a retainer, the inner bearing ring is formed into an annular outer ball raceway surface, left and right end surfaces of the annular outer ball raceway surface are formed into grooves and formed into concave and convex portions, the outer bearing ring is formed into three steps of L-shaped deformation in cross section of a left outer ring and a right outer ring which are divided into a cap shape, the left and right outer bearing rings are combined to form an annular ball cavity raceway surface having an annular ball shape space with an inner diameter dimension larger than the outer diameter dimension of the inner bearing ring as a first step, a second step of the left and right outer bearing rings is formed into a spherical inner ball raceway surface having an end portion with an inner diameter dimension identical to the outer diameter dimension of the inner bearing ring, and a third step is formed into an annular limit portion, the multiple rows of rolling bodies can be arranged between the outer ball raceway surface and the inner cavity raceway surface and between the left and right axial end surfaces of the inner ring and the annular limiting part in a rolling manner in a state of being held by the axially distributed retainers, and the inner ball raceway surface of the left and right outer bearing rings is in sliding fit with the outer ball raceway surface.

Description

Bearing, and rocking bearing device for reciprocating motion

The application is a divisional application, and the application numbers of the original application are as follows: 202010821664.X, filed on 2020, 08/15, entitled "rolling element bearing with angular motion freedom" is filed as a divisional application No.: 202110657765.2 entitled bearing, deflection bearing with controllable angular deviation and bearing device for wheel "

Technical Field

The invention relates to the technical field of combined bearings for general machinery, in particular to a swing bearing, relates to a swing bearing device for reciprocating motion, and also relates to a machine tool using the swing bearing device.

Background

The combined bearing is mainly used as a support shaft, can guide the rotation of a shaft and can also bear a mechanical part of force transmitted by the shaft.

The combined bearing is used in the fields of general machinery, such as rolling mills, underground drilling, crushing and grinding equipment, plunger pumps, internal combustion engines, electric tools, wind power equipment, helicopter rotor wing mechanisms and the like.

Wobble bearings are used in general purpose machines and reciprocating tools that are currently driven by electric motors, such as saber saws, hammer drills and the like, are typically driven by an electric motor having a rotating output shaft. The rotary motion is converted into a reciprocating motion of a working shaft for moving a saw blade or the like in a reciprocating manner. Various methods have been developed to convert rotational motion into reciprocating motion. The usual approach is to incorporate a wobble bearing drive. A swing bearing for use is disclosed in chinese patent CN 1853866B, and fig. 1 to 4 show a cross section of a swing device of the hammer drill. Fig. 1 to 4 show a section through a first embodiment of the pivoting device in fig. 1, the driven-side bearing region of which has a decreasing inner diameter on the side of the bearing region facing the working direction; FIG. 2 shows a section through a second embodiment of the pivoting device, the driven-side bearing region of which has a reduced inner diameter on the side of the bearing region facing away from the operating direction; FIG. 3 shows a section through a third embodiment of the wobble device, the drive-side bearing region of which has an increasing outer diameter on the side of the bearing region facing away from the operating direction; and fig. 4 shows a section through a fourth embodiment of the pivoting device, the drive-side bearing region of which has an increasing outer diameter on the side of the bearing region facing in the working direction. The outer surface 32 of the drive part 22 has a spherical basic shape and functions as a drive-side bearing region, in which a drive-side guide 34 for the rolling element 28 is formed around. Here, the drive-side guide 34 is positioned obliquely with respect to the drive shaft (axis) a of the intermediate shaft 24 or the drive element 22. At the same time, the driven part 26 has an inner wall 36 with a cylindrical basic shape, which acts as a driven-side bearing region, in the center of which a driven-side guide 38 for the rolling element 28 is formed. The inner wall 36 delimits a receiving cavity in which the drive member 22 is mounted. As shown in fig. 1 to 4, different embodiments of the pivot device 20 are used, in which the stability of the respective pivot bearing is increased by the basic shape of the bearing regions having an increased cross section on one side. However, when the oscillating bearing does work, the inner ring of the oscillating bearing rotates to drive the outer ring to oscillate, the balls roll in the raceway groove of the revolving gap between the inner ring and the outer ring under the action of reaction force, the friction between the edges of the two sides of the inner ring and the outer ring is large, the oscillating bearing is a drive for the peripheral edge part of the raceway groove with the inclined raceway of the inner ring, and the oscillating frequency is limited.

Another oscillating bearing for use is disclosed in chinese patent CN 104339031B, and fig. 5 and 6 show perspective and side views of the reciprocating drive mechanism of the reciprocating saw. As shown in fig. 5 and 6, the swing bearing 4 includes a first arm 5 and a second arm 11 at both ends thereof: the first arm 5 extends at an angle 17 to a plane defined by the first central axis a of the drive shaft 3 and the second central axis B of the spindle 7, such that the first arm 5 is in a mating connection with the spindle protrusion 6 of the spindle 7, such that the oscillating bearing 4 is capable of driving the spindle 7 to reciprocate; the second arm 11 extends in the same way counter to the first arm 5, so that the second arm 11 is in a mutually cooperating connection with the counterweight protrusion 12 of the counterweight 13, so that the pivot bearing 4 can at the same time also drive the counterweight 13 to reciprocate counter to the direction of movement of the spindle 7. Wobble bearing 4 further includes an inner race 41 and an outer race 42, inner race 41 being non-rotatably mounted relative to drive shaft 3, and a center axis of inner race 41 being disposed obliquely relative to first center axis a of drive shaft 3. The outer ring 42 is connected to the first arm 5 and the second arm 11. Between the inner ring 41 and the outer ring 42, raceways are provided in which balls 43 are arranged such that the inner ring 41 is rotatable relative to the outer ring 42. When the drive shaft 3 rotates the obliquely arranged inner ring 41, the outer ring 42 of the rocking bearing 4 reciprocates in the extending direction of the drive shaft 3. The first arm 5 and the second arm 11 of the oscillating bearing 4 are arranged in such a way that their direction of extension makes an angle 17 with the plane defined by the first central axis a of the drive shaft 3 and the second central axis B of the spindle 7, said angle 17 being between 10 ° and 45 °, when the direction of extension in which the first arm 5 and the second arm 11 are located and the plane defined by the first central axis a and the second central axis B make the angle 17, the spindle 7 can first of all be arranged closer to the drive shaft 3 in the overall structure than in the structure without making it, without any further consideration being given to the influence of the first arm 5 and the second arm 11 on the distance between the two. This means that the centre of gravity 16 of the spindle 7 can be located closer to the central axis of the drive shaft 3, thereby making the structure between the spindle 7 and the drive shaft 3 more compact; secondly, the connecting position between the balance weight 13 and the second arm 11 can be closer to the gravity center 15 of the balance weight 13, when the swing bearing 4 drives the balance weight 13 through the second arm 11, a torque acting force exists between the connecting position 12 and the balance weight 13 due to the smaller distance between the two, and further the torque acting on the guide rod 14 is reduced, so that the abrasion to the guide rod 14 is reduced; finally, the balancing effect of the reciprocating drive mechanism can be achieved in a better vibration reduction, since the distance between the center of gravity 16 of the spindle 7 and the center of gravity 15 of the balancing weight 13 can be brought closer together. Similarly, when doing work, the inner ring of the oscillating bearing rotates to drive the outer ring to oscillate, the balls roll in the revolving clearance raceway groove of the inner ring and the outer ring under the action of reaction force, the friction between the edges of the two sides of the inner ring and the outer ring is relatively large, the oscillating bearing is a drive for the peripheral edge part of the raceway groove with the inclined raceway of the inner ring, and meanwhile, the design and manufacturing cost is high.

Therefore, under the conditions of high performance, high precision and long service life requirements and high speed, heavy load and complex dynamic load environments, the self-adaptive adjustment cannot be carried out to prolong the service life of the oscillating bearing when the oscillating bearing is in motion fatigue wear failure, under the impact of reaction force, the contact between the inner ring and the outer ring which do linear reciprocating motion and the front surface of the rolling body has the outstanding advantage, and the existing oscillating bearing structure still needs to be improved.

Disclosure of Invention

The invention aims to provide a combined bearing for a general machine, a swinging bearing for the general machine and a machine tool of the swinging bearing device for reciprocating motion, which overcome the adaptability of the defects to complex load conditions, ensure high transmission stability and precision, low contact stress and long service life.

These objects have been achieved by the features as set forth in the independent claims. Advantageous embodiments of the invention can be found in the dependent claims and in the following description.

To those skilled in the art, the words axial and radial are frequently used in this document. If not otherwise stated, the axial direction is defined as the axial direction of the bearing parallel to its axis of rotation, the axial direction of the inner ring parallel to its axis of rotation, the axial direction of the outer ring parallel to its axis of rotation and the axial direction of the cage parallel to its axis of rotation. The radial direction is a direction perpendicular to the respective axial direction.

The invention adopts the technical scheme that the invention achieves the aim that: a combined bearing comprises an outer bearing ring (1), an inner bearing ring (2), a plurality of rows of rolling bodies (3), retainers (41-48) and fixing bolts (51), wherein the associated parts of the outer bearing ring (1) and the inner bearing ring (2) are spherical surfaces;

the inner bearing ring (2) is arranged in a circular ring shape, an outer ball raceway surface (21) is formed on the outer radial side surface of the circular ring shape, and a plurality of blind holes for retaining solid lubricant are formed in the outer ball raceway surface (21) of the inner bearing ring (2);

the outer bearing ring (1) further comprises a split left outer ring (11) and a split right outer ring (12), the left outer ring (11) and the right outer ring (12) are arranged in a cover ring shape, the left outer side of the cover ring-shaped left outer ring (11) extends inwards to form at least more than two steps, and the right outer side of the cover ring-shaped right outer ring (12) extends inwards to form at least more than two steps;

the first-stage steps (121, 122) of the outer bearing ring (1) are provided with radial spherical spaces with inner diameter sizes larger than the outer diameter sizes of the inner bearing ring (2), and the radial spherical spaces formed by connecting the first-stage steps (121, 122) left and right are formed into spherical inner cavity rolling surfaces (123, 124);

the combined end surfaces (125, 126) of the axial side walls of the first steps (121, 122) of the left outer ring (11) and the right outer ring (12) of the outer bearing ring (1) combination are positioned on a radial spherical center extension line and/or are offset relative to the radial spherical center extension line;

the outer bearing ring (1) is characterized in that second steps (131, 132) of the outer bearing ring (1) extend to an outer spherical surface raceway (21) of the inner bearing ring (2), inner ring end faces of the second steps (131, 132) in the left-right opposite radial direction form ring inner spherical raceway surfaces (133, 134), and outer side faces of the second steps (131, 132) in the left-right opposite axial direction form ring-shaped planes (143, 144);

the spherical inner cavity rolling surfaces (123, 124) and the spherical inner cavity rolling surfaces (133, 134) of the first steps (121, 122) and the second steps (131, 132) of the left outer ring (11, 12) and the right outer ring (11, 12) split by the outer bearing ring (1) are integrally formed into concentric upper and lower step spherical surfaces;

the diameters of the inner ball rolling surfaces (133, 134) of the second steps (131, 132) of the left and right outer bearing rings (11, 12) which are oppositely combined and penetrate through the sphere center are the same as the diameter of the outer ball rolling surface (21) of the inner bearing ring (2), the axial width of the outer bearing ring (1) is equal to 0.8-0.96 times of the axial width of the inner bearing ring (2) and/or the axial widths of the inner and outer rings (1, 2) are the same, and the inner ball rolling surfaces (133, 134) and the outer ball rolling surfaces (21) are formed into sliding motion;

the spherical inner cavity raceway surfaces (123, 124) and the inner annular ball raceway surfaces (133, 134) of the outer bearing ring (1) and the outer ball raceway surface (21) of the inner bearing ring (2) are spherical surfaces with coincident spherical centers, the distance (space) between the spherical inner cavity raceway surfaces (123, 124) and the outer ball raceway surface (21) can accommodate multiple rows of first rolling bodies (3), the multiple rows of first rolling bodies (3) are multiple rows of first rolling balls (31, 32), and the multiple rows of first rolling balls (31, 32) can be guided to roll between the spherical inner cavity raceway surfaces (123, 124) and the outer ball raceway surface (21);

the outer diameter of the outer ring on one side of the combined left and right outer bearing rings (11, 12) is slightly smaller than that of the outer ring on the other side, and/or the outer diameters of the outer rings on two sides of the combined left and right outer bearing rings (11, 12) are the same;

the periphery of the left outer ring (11) and the right outer ring (12) of the outer bearing ring (1) axially outside circular ring planes (143, 144) is relatively provided with eight staggered bolt counter bores (5), the bolt counter bores (5) penetrate through axial side walls (125, 126) of first-stage steps (121, 122) from the circular ring planes (143, 144) to the opposite surfaces, elastic pads (6) are arranged on the heads of the fixing bolts (51), and certain axial pretightening force is applied to the connection of the fixing bolts (51) to connect the outer bearing ring (1), multiple rows of first balls (31, 32) and the inner bearing ring (2) into a whole.

According to a further embodiment, the combination bearing,

set up multiseriate first ball (31, 32) between the outer ball raceway surface (21) of the ring ball inner chamber raceway surface (123, 124) of outer bearing circle (1) and inner bearing circle (2), multiseriate first ball (31, 32) set up two and/or more than two, multiseriate first ball (31, 32) axial is along annular spherical surface interval equipartition, wherein have at least two relative distribution of ball (31, 32) about the centre of sphere extension line in radial, control every ball (31, 32) of arranging according to the different quantity of ball of radial annular spherical surface diameter interval equipartition, the ring ball inner chamber raceway surface (123, 124) of multiseriate first ball (31, 32) axial distribution and outer ball raceway surface (21) of inner bearing circle (2) are the sphere of centre of sphere coincidence.

According to a further embodiment, the combination bearing,

the utility model discloses a ball cage, including the ball cage, the ball cage is characterized in that the first ball (31, 32) of multiseriate of axial interval equipartition set up the ball ring holder (41, 42) of axial interval equipartition, every row of ball (31, 32) sets up holder (41, 42) of equal quantity pocket relatively according to radial annular spherical diameter size about, the pocket of every row of holder (41, 42) is the bowl poroid, the bowl bottom hole of bowl poroid is towards the centre of sphere direction, every row of ball (31, 32) carries out the position through holder (41, 42) and keeps.

According to a further embodiment, the combination bearing,

the diameter of each ball of the left and right rows of first balls (31, 32) in the axial direction is larger than the distance from the inner ball encircling cavity raceway surface (123, 124) of the outer bearing ring (1) to the outer ball raceway surface (21) of the inner bearing ring (2), the value of the larger distance range is 0.003 mm-0.005 mm, and/or the diameter of each ball of the left and right rows of first balls (31, 32) in the axial direction is equal to the distance from the inner ball encircling cavity raceway surface (123, 124) of the outer bearing ring (1) to the outer ball raceway surface (21) of the inner bearing ring (2).

According to a further embodiment, the combination bearing,

the left and right side planes (221, 222) of the annular shaft of the inner bearing ring (2) are provided with plane raceways and/or channels (241, 242); and

the outer bearing ring (1) further comprises third-stage steps (141, 142) which further extend, the third-stage steps (141, 142) extend to form axial left and right side portions planes (221, 222) which are separated to partially wrap the inner bearing ring (2), axial inner side walls of the third-stage steps (141, 142) form annular limiting portions (145, 146), axial outer side faces of the third-stage steps (141, 142) form annular planes (143, 144) which replace axial outer side faces of the second-stage steps (131, 132), and channels (147, 148) and/or annular limiting portions (145, 146) are arranged in the annular limiting portions (145, 146) close to the middle portions and are provided with plane raceways;

each side of the first step (121, 122), the second step (131, 132) and the third step (141, 142) of the left outer ring (11, 12) and the right outer ring (11, 12) which are split by the outer bearing ring (1) is integrally formed; and

the ring-ball inner cavity rolling surfaces (123, 124), the ring-ball inner cavity rolling surfaces (133, 134) and the ring-shaped limiting parts (145, 146) in the outer bearing ring (1) are approximately L-shaped in cross section of the left and right hemispherical outer rings;

the curvature of the section curve of the raceway surface (147) of the annular limiting part (145) of the third step (141) of the left outer ring (11) and the curvature of the section curve of the raceway surface (241) of the left side surface (221) of the shaft of the inner bearing ring (2) are the same and are arranged in parallel relatively, and the curvature of the section curve of the raceway surface (148) of the annular limiting part (146) of the third step (142) of the right outer ring (12) and the curvature of the section curve of the raceway surface (242) of the right side surface (222) of the shaft of the inner bearing ring (2) are the same and are arranged in parallel relatively;

two rows of second rolling bodies (3) are arranged at the distance (space) from the plane raceways of the third-stage step (141, 142) annular limiting parts (145, 146) of the left and right outer rings (11, 12) of the outer bearing ring (1) to the plane raceways of the left and right side surfaces (221, 222) of the shaft of the inner bearing ring (2), the two rows of second rolling bodies (3) are two rows of second cylindrical rollers (351, 352), the two rows of second cylindrical rollers (351, 352) are held by axial retainers (47, 48), and the two rows of second cylindrical rollers (351, 352) can be guided to roll between the plane raceway surfaces (221, 222) of the inner ring (2) and the plane raceway surfaces (145, 146) of the outer ring (1).

According to a further embodiment, the combination bearing,

the axial cage for holding two rows of second cylindrical rollers (351, 352) is an annular window type cage (47, 48), the section of the annular window type cage (47, 48) is approximately T-shaped, one side of the upper part of the T-shaped is extended to the axial plane raceway surfaces (221, 222) of the inner ring (2), the other side of the upper part of the T-shaped is extended to two positions of the axial plane raceway surfaces (145, 146) and the radial inner diameter end parts of the third step (141, 142) of the outer ring (1) to form L-shaped joint parts (471, 481), the lower part of the T-shaped is formed into uniformly distributed window type pockets (472, 482), the pockets (472, 482) of the window type cage (47, 48) are arranged on a plane relative to the raceway surfaces on two sides of the cylindrical rollers (351, 352), and the other two sides of the window type cage (47, 48) are arranged on parallel arc surfaces; the left side and the right side of the outer diameter surface of the annular window type retainer T-shaped upper part extending axially can be sleeved with rubber sealing rings.

According to a further embodiment, a rocking bearing,

axial convex parts and concave parts (151, 153, 152 and 154) are arranged on annular limiting parts (145 and 146) of third-stage steps (141 and 142) of the left outer ring (11) and the right outer ring (12) in a linear matching mode, the convex part (153) of the annular limiting part (145) of the left outer ring (11) is arranged relative to the concave part (154) of the annular limiting part (146) of the right outer ring (12), the concave part (151) of the annular limiting part (145) of the left outer ring (11) is arranged relative to the convex part (153) of the annular limiting part (146) of the right outer ring (12), the convex-concave part (151 and 153) of the annular limiting part (145) of the third-stage step (141) of the left outer bearing ring (11) is arranged relative to the concave-convex part (152 and 154) of the annular limiting part (146) of the third-stage step (142) of the right outer bearing ring (12), and the annular limiting parts (145 and the third-stage steps (141 and 142) of the left outer bearing ring (11 and right outer bearing ring (12) are arranged in a linear matching mode, 146) The curvatures of the curves of the convex-concave parts (151, 153, 152, 154) are the same, the left and right side surfaces (221, 222) in the axial direction of the inner bearing ring (2) are arranged in parallel relative to the convex-concave parts (151, 153, 152, 154) of the annular limiting parts (145, 146) of the third step (141, 142) of the left and right outer rings (11, 12) of the outer bearing ring (1), and the left and right side surfaces (221, 222) in the axial direction of the inner bearing ring (2) are provided with channels (241, 242);

the distance (space) from the convex-concave parts (151, 153, 152, 154) of the straight lines of the third-stage steps (141, 142) of the left outer ring (11) and the right outer ring (12) to the grooves (241, 242) of the left side surface (221, 222) and the right side surface (145, 146) of the inner bearing ring (2) is provided with third rolling bodies (321, 322), the third rolling bodies (321, 322) are left and right rows of third balls (321, 322), each row of the third balls (321, 322) is a cross shape formed by four axial cage pockets, the diameters of the balls of the four cross-shaped balls (321, 322) are the same, the radius of the balls of each row of the third balls (321, 322) is slightly smaller than the curvature of the section curves of the convex parts and the concave parts (151, 153, 152, 154), and the two rows of the cross-shaped third balls (321, 322) can be guided to the left and the inner ring (2), The channels (241, 242) on the right side surfaces (221, 222) roll with the annular limiting parts (145, 146) and the linear concave-convex parts (151, 153, 152, 154) of the outer ring (1); and/or

The annular limiting parts (145, 146) of the third-stage steps (141, 142) of the left and right outer rings (11, 12) are provided with channels (147, 148), the axial left and right side surfaces (221, 222) of the inner bearing ring (2) are provided with axial convex parts and concave parts in a linear matching manner, the convex part (263) of the left side surface (221) of the inner ring (2) is configured relative to the concave part (264) of the right side surface (222) of the inner ring (2), the concave part (261) of the left side surface (221) of the inner ring (2) is configured relative to the convex part (262) of the right side surface (222) of the inner ring (2), the linear convex-concave parts (263, 261) of the left side surface (221) of the inner ring (2) are configured relative to the linear concave-convex parts (264, 262) of the right side surface (222) of the inner ring (2), and the curvatures of the linear convex-concave parts (263, 261, 264) of the axial left and right side surfaces (221) of the inner bearing ring (2) are the same, the axial left and right side surfaces (221, 222) of the inner bearing ring (2) are provided with linear convex-concave parts (263, 261, 264, 262) which are arranged in parallel relative to the channels (147, 148) of the third-stage steps (141, 142) of the annular limiting parts (145, 146) of the left and right outer rings (11, 12) of the outer bearing ring (1);

the distance (space) from the channels (147, 148) of the annular limiting parts (145, 146) of the third-stage steps (141, 142) of the left outer ring (11) and the right outer ring (12) to the linear convex-concave parts (263, 261, 264 and 262) of the left side surface and the right side surface (221, 222) of the inner bearing ring (2) is provided with third rolling bodies (321, 322), the third rolling bodies (321, 322) are left and right rows of third balls (321, 322), each row of the third balls (321, 322) is a cross shape formed by four pockets of axial retainers (43, 44) in a surrounding mode, the diameters of the four balls in the two rows of cross shape are the same, the radius of the balls in each row of the third balls (321, 322) is slightly smaller than the curvature of the section curves of the convex-concave parts (263, 261, 264 and 262), and the two rows of the cross-shaped third balls (321, 322) can be guided to the left side surface and the right side surface (221) of the inner ring (2), 222) And the linear convex-concave parts (263, 261, 264 and 262) and the channels (147 and 148) of the annular limiting parts (145 and 146) of the outer ring 1 roll.

According to a further embodiment, a rocking bearing,

the central axes of the axial left and right side surfaces (221, 222) of the inner bearing ring (2) are obliquely arranged relative to the axis of the transmission shaft, and the axial left and right oblique side surfaces (231, 232) of the inner bearing ring (2) are relatively arranged in parallel;

two rows of second rolling bodies (3) are arranged at the distance (space) from the plane raceways of the annular limiting parts (145, 146) of the third-stage steps (141, 142) of the left and right outer rings (11, 12) of the outer bearing ring (1) to the plane raceways of the left and right inclined side surfaces (231, 232) of the shaft of the inner bearing ring (2), the two rows of second rolling bodies (3) are two rows of second cylindrical rollers (351, 352), the two rows of second cylindrical rollers (351, 352) are held by axial retainers (47, 48), and the two rows of second cylindrical rollers (351, 352) can be guided to roll between the inclined plane raceway surfaces (231, 232) of the inner ring (2) and the plane raceway surfaces (145, 146) of the outer ring (1).

According to a further embodiment, a rocking bearing,

the central axes of the axial left and right side surfaces (221, 222) of the inner bearing ring (2) are obliquely arranged relative to the axis of the transmission shaft, and the axial left and right oblique side surfaces (231, 232) of the inner bearing ring are relatively arranged in parallel;

two rows of fourth rolling bodies (341 and 342) are arranged at the distance (space) from the left and right inclined side surfaces (231 and 232) of the inner bearing ring (2) to the grooves (147 and 148) of the third step (141 and 142) of the annular limiting parts (145 and 146) of the left and right outer rings (11 and 12) of the outer bearing ring (1), the two rows of fourth rolling bodies (341 and 342) are annular slope balls (341 and 342) with an angle, each row of annular slope balls (341 and 342) is in interval transition from small-diameter balls (332 and 333) to large-diameter balls (331 and 334), and the balls arranged from the large diameter to the small diameter are held by pockets with different sizes of axial retainers (45 and 46); each ball with different diameters of each row of annular slope balls (341, 342) is a ball which is opposite to each other and is the same on the same straight line, and the gradient of each annular slope ball (341, 342) is 3-15 degrees;

the left and right rows of fourth annular slope balls (341 and 342) are the same, the axial distance of the slope balls (341) of the left row of balls is equal to the distance from the raceway (147) of the annular limiting part (145) of the third step (141) of the left outer ring (11) to the axial left inclined surface (231) of the inner bearing ring (2), and the axial distance of the slope balls (342) of the right row of balls is equal to the distance from the raceway (148) of the annular limiting part (146) of the third step (142) of the right outer ring (12) to the axial right inclined surface (232) of the inner bearing ring (2);

the radius of the axial channels (147, 148) of the outer bearing ring (1) is slightly larger than that of the large-diameter balls (331, 334) of the fourth annular ramp balls (341, 342);

the large-diameter ball (331) of the left row of balls (341) of the fourth annular slope balls (341 and 342) is relative to the small-diameter ball (332) of the right row of balls (342), one axial ball contact point of the annular slope balls (341 and 342) is tangent to the raceways (147 and 148) of the third-stage steps (141 and 142) of the left and right outer rings (11 and 12) and the annular limiting parts (145 and 146), and the other axial ball contact point of the annular slope balls (341 and 342) is tangent to the left and right inclined side surfaces (231 and 232) of the inner bearing ring (2).

According to a further embodiment, the oscillating bearing device (8),

swing bearing's outer race (1) of external diameter big left outer lane (11) cup joint set up swing arm (9), swing arm (9) are provided with sleeve (91), set up two bolt holes on sleeve (91), sleeve (91) are connected and are fixed with bolt (93) on left outer lane (11), the tip of the arm that swing arm (9) extend forms pole (92).

In an embodiment of the invention a combination bearing and rocking bearing is proposed, wherein the cage is a radial ball ring bowl cage, an axial ball bore cage for the balls and an axial window cage for the cylindrical rollers. In embodiments, the cage is made of a polymer, a metal such as brass, steel or iron, or any other suitable material recognized by those skilled in the art.

Other embodiments and modifications to the present embodiments presented herein within the scope of the claims will be apparent to those skilled in the art. For example, those skilled in the art will understand and appreciate that the cage pocket geometry may be designed differently to still achieve the same effect.

Compared with the prior art, the invention has the beneficial effects that:

(1) the outer ring of the oscillating bearing is divided into two parts, wherein the outer side of the outer ring of each part is provided with three steps on the raceway surface of the outer ball of the inner ring. Each row of balls in the inner cavity raceway surface is retained in position by an axial retainer. The pretightening force adjustment among the outer ring, the rolling body and the inner ring is realized by adjusting the left outer ring, the right outer ring and the multiple rows of rolling bodies through fixing screws, the fit degree of a radial gap and an axial gap of the bearing can be accurately controlled, and the radial gap and the axial gap can be adjusted to be in a basically consistent state. Therefore, the bearing precision is improved, and the influence of the motion precision of the bearing on the motion precision of the mechanism is reduced.

(2) The invention can flexibly combine through the diameter change of each ball of each row of balls in the inner cavity raceway surface of the bearing and the axial distance change of the left outer ring and the right outer ring of the bearing, each row of balls is axially arranged left and right according to the diameter of the annular spherical surface, the change of the axial diameter when the left outer ring and the right outer ring are connected is about the same as the diameter of the outer bearing ring, when the bearing rotates with angular freedom, each row of balls in the inner cavity raceway surface is in multi-point multi-line contact with the raceways of the inner ring and the outer ring, the raceways can rotate with the angular freedom which is self-adaptive along with the change of external force, and the contact stress is high. When outer race, multiseriate rolling element and interior race kinematic fatigue wearing and tearing, the diameter of three is changing, and the external diameter of the left outer lane of the outer lane is greater than the external diameter of right outer lane about outer race combination, through the flexible combination of hemisphere outer lane, the hemisphere outer lane that the external diameter is big and bearing box interference fit, the automatic flexible pretension of the hemisphere outer lane that the external diameter is little, and the bullet pad on the fixed screwhead has an elasticity to make outer race, multiseriate rolling element and interior race be in the same place all the time. The first is that rolling and sliding move simultaneously after the rolling movement is worn out; the second is the simultaneous movement of scrolling and sliding. Under the action of dynamic load, obvious stress concentration occurs on a part of a contact part of each row of balls in an inner cavity raceway surface and the raceway, for example, on a bearing with a nominal point contact center, a line contact end part and no accurate ball guide, the initial defects occur on the surfaces of the balls, and the bearing cannot be out of work by combining different motion modes.

(3) According to the invention, the influence of reciprocating rotary motion on precision can be provided by eliminating gaps through a plurality of rows of axial rolling bodies, and according to the motion speed and load, when rolling motion fatigue wear occurs, the axial distance gap between the left outer ring and the right outer ring of the bearing is reduced, and the inner spherical raceway of the second step on the outer bearing ring and the outer spherical raceway surface of the inner bearing ring start sliding friction; the rolling device can also be provided with a sliding mechanism and a rolling mechanism which move simultaneously, wherein an inner cavity raceway surface of the outer bearing ring, an outer ball raceway surface of the inner bearing ring, an axial raceway of the outer bearing ring, an axial end surface of the inner bearing ring and a plurality of rows of rolling bodies are in rolling friction, and an inner spherical raceway of the second-stage step on the outer bearing ring and an outer ball raceway surface of the inner bearing ring are in rolling friction. The ball bearing can be used in a motion mechanism with higher precision requirement by the diameter of the ball and the arrangement of the inner cavity raceway surfaces of the outer rings of the left hemisphere and the right hemisphere, so that the influence of the clearance of the oscillating bearing on the motion precision and the return difference is avoided, and particularly the high-precision space direction mechanism is avoided.

(4) The invention adopts different designs: firstly, arranging axial convex-concave parts of third-stage steps of a left outer ring and a right outer ring of an outer bearing ring, arranging a raceway of an axial end face of an inner bearing ring and arranging four crossed balls, wherein the inner ring rotates to drive the outer ring to swing towards one direction and then return to the positive direction in a motion mode which is the same as that of a cam;

the axial end face of the inner bearing ring is obliquely arranged and the axial cylindrical roller is arranged, the inner ring rotates to drive the outer ring to do linear reciprocating motion, the axial cylindrical roller is in contact with the axial front face of the inner ring and the axial front face of the outer ring, the contact stress is high, and the anti-impact capability is strong;

and thirdly, the axial end face of the inner bearing ring is inclined and the annular slope balls are arranged, the rotating axial inclined end face of the inner bearing ring positively drives the outer bearing ring to swing (the annular slope balls roll on the axial end face of the inner ring and the outer ring), the motion mode is that the inner ring rotates to drive the outer ring to perform torsional precession motion, the swinging angle and the swinging frequency of the swinging bearing can be limited by the above motion, meanwhile, the pockets of the radial retainer are deviated to the inner bearing ring relative to the multiple rows of balls in the raceway surface of the inner cavity of the annular ball, and when the angular rotation of the inner bearing ring of the swinging bearing deviates the multiple rows of balls, the pockets of the retainer can be matched with the outer bearing ring to keep the relative position of each ball unchanged.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:

fig. 1 to 4 show a cross section of a wobble device of a percussion drill according to one embodiment of the prior art.

Fig. 5 to 6 show perspective and side views of a reciprocating drive mechanism of a reciprocating saw according to another embodiment of the prior art.

Fig. 7 shows a front view of a combination bearing according to a first embodiment of the invention.

Fig. 8 shows a section E-E of a combination bearing according to a first embodiment of the invention according to fig. 7.

Fig. 9 shows a side view of a combination bearing according to a first embodiment of the invention.

Fig. 10 shows a section F-F of a combination bearing according to a first embodiment of the invention according to fig. 9.

Fig. 11 shows an exploded view of a combination bearing according to a first embodiment of the present invention.

Fig. 12 shows a partial view of the cylindrical roller axial cage of the first embodiment combination bearing according to the invention according to fig. 8.

Fig. 13 shows a sectional view of a rocking bearing according to a second embodiment of the invention.

FIG. 14 is a cross-sectional view of the left and right axial balls of a rocking bearing according to a second embodiment of the present invention rotated onto the concave and convex portions of the outer race to rock the outer race by an angle B.

Fig. 15 shows an exploded view of the left and right axial balls of a wobble bearing according to a second embodiment of the invention turning onto the recesses and protrusions of the outer race.

Fig. 16 shows a cross section of a rocking bearing according to a third embodiment of the invention.

Fig. 17 shows an exploded view of a rocking bearing according to a third embodiment of the invention.

FIG. 18 is a cross section according to FIG. 16 showing the left and right axial ramp balls of the rocking bearing of the third embodiment of the present invention rotated 180 to rock the outer race by an angle A.

Fig. 19 shows a front view of a rocking bearing according to a fourth embodiment of the invention.

FIG. 20 shows a sectional view through G-G of a rocking bearing according to a fourth embodiment of the invention in accordance with FIG. 19.

Fig. 21 shows a side view of a rocking bearing according to a fourth embodiment of the invention.

Figure 22 shows a sectional view H-H of a rocking bearing according to a fourth embodiment of the invention according to figure 21.

Fig. 23 shows an exploded view of a rocking bearing according to a fourth embodiment of the invention.

FIG. 24 is a partial view of the cylindrical roller axial cage of the rocking bearing of the fourth embodiment of the invention according to FIG. 20.

FIG. 25 FIG. 26 FIG. 27A combined bearing and fourth embodiment rocking bearing according to the first embodiment shows a fifth embodiment of the invention in a view of a disassembled cylindrical roller axial cage mounting one roller.

Fig. 28 shows a sectional view of a rocking bearing according to a sixth embodiment of the invention.

FIG. 29 is a sectional view showing the rocking bearing of the sixth embodiment of the present invention in another direction in which the two rows of the third balls roll on the inner ring concavo-convex portion according to FIG. 28.

Fig. 30 is a perspective view showing a swing bearing device mounting a swing arm according to a seventh embodiment of the present invention according to the second, third, and fourth embodiments.

Description of the symbols

1. The outer bearing ring 11, the left outer ring, 12, the right outer ring, 141, the third step of the left outer ring, 142, the third step of the right outer ring, 143, the circular ring plane of the third step, 144, the circular ring plane of the third step of the right outer ring, 145, the annular limiting part of the third step of the left outer ring, 146, the annular limiting part of the third step of the right outer ring, 151, the concave part of the annular limiting part of the third step of the left outer ring, 152, the convex part of the annular limiting part of the third step of the right outer ring, 153, the convex part of the annular limiting part of the third step of the left outer ring, 154, the concave part of the annular limiting part of the third step of the right outer ring

131. A second step of the left outer ring, 132. a second step of the right outer ring, 133. an inner ball raceway surface of the second step of the left outer ring, 134. an inner ball raceway surface of the second step of the right outer ring, 135. a side wall of the second step of the left outer ring, 136. a side wall of the second step of the right outer ring,

121. the first step of the left outer ring, 122, the first step of the right outer ring, 123, the rolling surface of the spherical inner cavity of the first step of the left outer ring, 124, the rolling surface of the spherical inner cavity of the first step of the right outer ring, 125, the axial end surface of the first step of the left outer ring, 126, the axial end surface of the first step of the right outer ring,

2. inner bearing ring, 21. outer ball raceway surface, 221. axial left side plane, plane rolling of inner bearing ring, 222. axial right side plane, plane rolling of inner bearing ring,

231. an axial left inclined surface of the inner bearing ring, an axial right inclined surface of the 232 inner bearing ring, 241, an axial left raceway groove of the inner bearing ring, 242, an axial right raceway groove of the inner bearing ring,

261 inner ring axial left side surface recess, 263 inner ring axial left side surface projection, 262 inner ring axial right side surface projection, 264 inner ring axial right side surface recess

3. Multiple rows of rolling elements, 31, left first ball in cavity, 32, right first ball in cavity, 321, axial side left third ball, 322, axial side right third ball, 341, axial side left fourth ramp ball, 342, axial side right fourth ramp ball, 331, left fourth ramp ball large diameter ball 333, left fourth ramp ball small diameter ball

332. Major diameter ball 334 of right fourth ramp ball, minor diameter ball of right fourth ramp ball

351. Axial left second cylindrical roller, 352 axial right second cylindrical roller

41. Left first ball retainer in cavity, 41 right first ball retainer in cavity, 43 axial left third ball retainer, 44 axial right third ball retainer 45 left fourth ramp ball retainer, 46 right fourth ramp ball retainer, 47 left second annular window retainer, 48 right second annular window retainer

471. Left annular window cage engagement 481

472. Pocket 482 of Window cage pocket of Window cage

51. Fixing bolt, 5. bolt counter bore

6. Spring pad

8. Oscillating bearing device

9. Swing arm, 91 sleeve, 92 round bar, 93 bolt

Detailed Description

It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict. The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.

First embodiment

As shown in fig. 7 to 12, the invention relates to a combined bearing.

The combined bearing is applied to general machinery, such as rolling mills, underground drilling, crushing and grinding equipment, plunger pumps, internal combustion engines, electric tools, wind power equipment, helicopter rotor wing mechanisms and other fields.

The combined bearing according to the first embodiment of the bearing shown in fig. 7 to 12 includes an outer bearing ring 1 and an inner bearing ring 2 coaxial with the outer bearing ring 1 and having a spherical center, and the multi-row rolling elements 3 may be formed such that at least two rows of

first balls

31 and 32 are arranged on the left and right sides across a radial line of the spherical center in a radial direction in the rolling contact surface of the spherical inner cavity, and two rows of second cylindrical rollers 351 and 352 on the left and right sides of the

annular stopper portions

145 and 146 of the

third steps

141 and 142 are arranged in the axial direction, and the

cages

41, 42, 47, and 48 are provided.

The inner bearing ring 2 is formed in an annular shape, an outer ball raceway surface 21 is formed on an outer spherical surface thereof, a plurality of blind holes for retaining a solid lubricant are formed in the outer ball raceway surface 21 of the inner bearing ring 2, and flat raceways are formed on left and right axial side surfaces 221 and 222 thereof.

The outer bearing ring 1 forms a three-stage step with L-shaped cross sections which are divided into a left outer ring 11 and a right outer ring 12 which are in cover ring shapes; the outer diameter of the outer ring on one side of the combined left and right outer bearing rings 11 and 12 is smaller than that of the outer ring on the other side, or the outer diameters of the outer rings on both sides of the combined left and right outer bearing rings 11 and 12 are the same; the first steps 121, 122 of the three steps of the left and right outer bearing rings 11, 12 are combined to form a toroidal-spherical space having an inner cavity with an inner diameter size larger than the outer diameter size of the inner bearing ring 2, and the first steps 121, 122 are formed as toroidal-spherical inner cavity raceway surfaces 123, 124 in the toroidal-spherical space thereof; the second steps 131, 132 of the left and right outer bearing rings 11, 12 are formed into inner spherical shapes having the same inner diameter dimension as the outer diameter dimension of the inner bearing ring 2, and the second steps 131, 132 are formed into inner spherical raceway surfaces 133, 134 at the inner spherical end portions thereof; axial inner side walls of third steps 141 and 142 of left and right hemispherical outer rings 11 and 12 of an outer bearing ring 1 are formed into annular limiting parts 145 and 146 to be provided with plane raceways, axial outer side faces of the third steps 141 and 142 are formed into annular planes 143 and 144, the peripheries of the annular planes 143 and 144 are provided with eight staggered bolt counter bores 5, and the annular planes 143 and 144 pass through the axial side walls 125 and 126 of the first steps 121 and 122 to opposite faces; the third steps 141, 142 and the second and first steps 131, 132, 121, 122 of the left and right hemispherical outer rings 11, 12 of the outer bearing ring 1 form a cover ring-shaped step which is connected into a whole, the spherical inner cavity raceway surfaces 123, 124 and the spherical inner raceway surfaces 133, 134 are spherical upper and lower raceways, and the axial inner side walls of the annular limiting parts 145, 146 are provided with plane raceways; the axial left and right end faces 125, 126 of the first steps 121, 122 of the combination of the left outer ring 11 and the right outer ring 12 of the outer bearing ring 1 are on or offset from the spherical center ray in the radial direction; the outer bearing ring 1 and the outer ball raceway surface 21 of the inner bearing ring 2 are arranged on the same sphere center through the ring ball inner cavity raceway surfaces 123 and 124; the first balls 31, 32 and the second cylindrical rollers 351, 352 in two rows are rollably arranged between the outer ball raceway surface 21 and the toroidal inner cavity raceway surfaces 123, 124 of the outer bearing ring 1 and between the left and right side surfaces 221, 222 in the axial direction and the annular stopper portions 145, 146 in a state of being axially spaced apart by the retainers 41, 42, 47, 48.

The axial cages for holding two rows of second cylindrical rollers 351 and 352 are annular

window type cages

47 and 48, the sections of the annular

window type cages

47 and 48 are approximately T-shaped, one side of the upper part of the T-shaped cage extends to the axial plane raceway surfaces 221 and 222 of the inner ring 2, the other side of the upper part of the T-shaped cage extends to the axial

plane rolling surfaces

145 and 146 and the radial inner diameter end parts of the

third step

141 and 142 of the outer ring 1 to form L-shaped joint parts 471 and 481, the lower part of the T-shaped cage is formed into uniformly distributed window type pockets 472 and 482, the pockets 472 and 482 of the

window type cages

47 and 48 are arranged on a plane relative to the rolling surfaces of two sides of the cylindrical rollers 351 and 352, and the other two sides of the

window type cages

47 and 48 are provided with parallel arc-shaped surfaces; rubber sealing rings can be sleeved on the left side and the right side of the outer diameter surface of the T-shaped upper part of the annular

window type retainers

47 and 48, which axially extends.

The spherical centers of the spherical inner cavity raceway surfaces 123 and 124, the inner spherical raceway surfaces 133 and 134 of the outer bearing ring 1 and the outer spherical raceway surface 21 of the inner bearing ring 2 coincide, a plurality of blind holes for retaining solid lubricants are formed in the outer spherical raceway surface 21 of the inner bearing ring 2, and the inner spherical raceway surfaces 133 and 134 of the

second steps

131 and 132 of the left and right outer bearing rings 11 and 12 and the outer spherical raceway surface 21 of the inner bearing ring 2 are in contact sliding friction fit.

A space for accommodating the plurality of rows of

first balls

31 and 32 is provided between the spherical inner cavity raceway surfaces 123 and 124 of the combination of the left outer ring 11 and the right outer ring 12 and the outer ball raceway surface 21 of the inner bearing ring 2. The inner

ball rolling surfaces

123 and 124 and the outer ball rolling surface 21 can contain a plurality of rows of

first balls

31 and 32 and enable the first balls to roll in two spherical rolling paths, in order to keep the relative positions of the plurality of rows of

first balls

31 and 32,

retainers

41 and 42 of a radial annular spherical surface are added, the

retainers

41 and 42 are matched with the left outer bearing ring 11 and the right outer bearing ring 12 to enable the axial annular spherical surfaces of the two rows of

first balls

31 and 32 to be uniformly distributed at intervals, and the relative positions of the

balls

31 and 32 in each row can be ensured not to change in the rolling process; the

retainers

41 and 42 are made of polytetrafluoroethylene retainers which have a certain self-lubricating function and can lubricate the balls, the

retainers

41 and 42 are made of spherical ring structures, pockets for accommodating steel balls are uniformly distributed on the spherical ring structures, and the pockets of each row of

retainers

41 and 42 are deviated from the outer spherical raceway surface 21 of the inner bearing ring 2 relative to each row of

balls

31 and 32.

The distance of the side walls 135 and 136 of the opposite second steps 131 and 132 of the left outer ring 11 and the right outer ring 12 of the outer bearing ring 1 is set, so that two rows of first balls 31 and 32 can freely rotate in the rolling surfaces 123 and 124 of the inner ball cavity, when the angular deflection is relatively large, the two rows of balls 31 and 32 can be in contact with the axial side walls 135 and 136 of the retainers 41 and 42, meanwhile, the pockets of the retainers 41 and 42 are deviated from the inner bearing ring 2 relative to the two rows of balls 31 and 32, and when the rotating angle of the inner bearing ring 2 of the combined bearing is deviated from the two rows of balls 31 and 32, the pockets of the retainers 41 and 42 can be matched with the outer bearing ring 1 to keep the relative position of each ball unchanged; further, the distance from the inner side wall annular limiting portions 145 and 146 of the third steps 141 and 142 of the left and right outer rings 11 and 12 of the outer bearing ring 1 to the axial left and right side surfaces 221 and 222 of the inner bearing ring 2 can accommodate two rows of second cylindrical rollers 351 and 352, each roller of the left and right rows of second cylindrical rollers 351 and 352 has a diameter equal to the distance from the left and right inner side wall annular limiting portions 145 and 146 to the axial left and right side surfaces 221 and 222 and rolls on the two plane raceways 145, 146, 221 and 222, and further limits the rotation of the combined bearing of the first embodiment at radial 0 degrees.

The combined bearing is assembled according to the operable sequence that the right outer ring 12 with small outer diameter of the outer bearing ring 1 is flatly placed on a workbench, the right one-row second cylindrical roller 352 on the right side in the axial direction of the second step is placed in a plane raceway of the annular limiting part 146 on the inner side wall of the third step 142 of the right outer ring 12 with small outer diameter, the right one-row first ball 32 in the inner cavity raceway surface 124 is assembled in the third step, the inner bearing ring 2 is assembled in the fourth step and placed in two rows of rolling bodies 352 and 32 in the right outer ring 12, the fifth step is to use a T-shaped round rod to penetrate through a mandrel of the inner bearing ring 2, the assembled half of the right outer ring 12, the two rows of rolling bodies 352 and 32 and the assembled half of the assembly of the left outer ring 11 with large outer diameter and the two rows of rolling bodies 351 and 31 are reversely buckled in the other half of the assembly of the left outer ring 11 and the right outer ring 12, and finally the left outer ring 11 and the right ring 12 are connected and fixed in a pre-tightening way by the bolts 51.

There are two kinds of movement modes according to different combined bearings: first, rolling → rolling plus sliding, fig. 7 to 11 are assembled as above, the diameters of the in-ring ball raceway surfaces 133, 134 of the opposing

second steps

131, 132 of the left and right outer rings 11, 12 of the outer bearing ring 1 passing through the center of the sphere are equal to the diameters of the outer ball raceway surfaces 21 of the inner bearing ring 2; the

first balls

31, 32 of each left and right row of the radial extension line on the sphere center are axially arranged oppositely left and right, the diameter of each ball of each left and right opposite row of the

first balls

31, 32 is larger than the distance from the rolling

surface

123, 124 of the inner cavity of the ring ball to the rolling surface 21 of the outer ball, and the larger value is in a data range of 0.003 mm-0.005 mm. Then, according to the axial clearance between the left and right outer bearing rings 11, 12, the fixing screw 51 applies a pre-tightening force to adjust the moment of the elastic pad 6, so that the purpose of accurately adjusting the clearance between the left and right rows of

first balls

31, 32 and the inner

ball rolling surfaces

123, 124 of the ring ball and the outer ball rolling surface 21 can be achieved. At outer race 1, when multiseriate rolling element 3 and the 2 sports fatigue wearing and tearing of inner race, the diameter of three is changing, the external diameter of the left outer lane 11 of the hemisphere outer lane of the 1 combination of outer race is greater than the external diameter of right outer lane 12, through the flexible combination of hemisphere outer lane, the hemisphere outer lane 11 and the bearing box interference fit that the external diameter is big, the automatic flexible pretension of hemisphere outer lane 12 that the external diameter is little, the overhead bullet pad 6 of fixing bolt 51 has an elasticity to make outer race 1, multiseriate rolling element 3 and inner race 2 are fixed together all the time. Through the adjustment, the original spherical contact is changed into the rolling contact of the multiple rows of rolling bodies 3, and on one hand, the gaps between the multiple rows of rolling bodies 3 and the inner bearing ring 2 and the gaps between the multiple rows of rolling bodies 3 and the left outer ring 11 and the right outer ring 12 can be adjusted automatically through the torque of the pretightening force of the elastic pad 6 of the fixing screw 51. After the rolling elements 3 in the left and right rows in the axial direction wear due to fatigue, the inner ball raceway surfaces 133 and 134 and the outer ball raceway surface 21 make sliding motion. On the other hand, the original bearing rolling friction is changed into the rolling and sliding friction of the rolling joint bearing. Through the change, firstly, the gap is accurately controlled, and meanwhile, a certain pretightening force can be applied to achieve the aim of no gap, so that the movement precision is improved; and secondly, rolling friction and sliding friction are combined, so that the coefficient of the rolling friction can be effectively reduced, the service life of the bearing is prolonged, and particularly the service life of the bearing under the conditions of heavy load and high speed is prolonged.

Secondly, sliding and rolling are simultaneously moved, fig. 7 to 11 are assembled as above, and the diameters of the spherical inner cavity raceway surfaces 123 and 124 of the outer bearing ring 1 and the outer ball raceway surface 21 of the inner bearing ring 2 may be set to be the same as the spherical inner and outer diameters of the distributed right and left rows of first balls 31 and 32 (the diameter of each ball of the right and left rows of

first balls

31 and 32 is equal to the distance from the inner cavity raceway surfaces 123 and 124 to the outer ball raceway surface 21). The diameters of the inner ball raceway surfaces 133 and 134 of the second step of the outer bearing ring 1 and the outer ball raceway surface 21 of the inner bearing ring 2 are the same, the outer bearing ring 1, the left and right rows of

first balls

31 and 32 and the inner bearing ring 2 are concentric, and a pretightening force is applied to eight opposite fixing screws 51 of the left and right outer bearing rings 11 and 12, so that the elastic pad 6 has a certain moment, and the outer bearing ring 1, the multiple rows of rolling

bodies

31 and 32, 351 and 352 and the inner bearing ring 2 are fixed to slide and roll integrally and move simultaneously.

Second embodiment

Fig. 13, 14 and 15 show a rocking bearing designed according to the present invention.

The oscillating bearing is applied to the fields of general machinery, electric tools and the like. Reciprocating tools that are currently driven by a motor, such as hammer drills, power nailers, and the like, are typically driven by a motor having a rotating output shaft. The rotary motion is converted into a reciprocating motion of a working shaft for moving a drill bit or the like in a reciprocating manner. Various methods have been developed to convert rotational motion into reciprocating motion. The usual approach is to incorporate a wobble bearing drive.

The rocking bearing according to the second embodiment of the bearing shown in fig. 13 to 15 includes an outer bearing ring 1 and an inner bearing ring 2 coaxial with the outer bearing ring 1 and having a spherical center, and the rolling elements 3 may be formed in a plurality of rows such that at least two rows of

first balls

31 and 32 are arranged on the right and left sides across a radial line of the spherical center in a radial direction in a rolling surface of a rolling element ring cavity and at least two rows of

third balls

321 and 322 are arranged on the right and left sides of

annular stoppers

145 and 146 of

third steps

141 and 142 in an axial direction, and the

retainers

41, 42, 43, and 44 are provided.

The inner bearing ring 2 is formed in an annular shape, an outer ball raceway surface 21 is formed on an outer spherical surface thereof, a plurality of blind holes for retaining a solid lubricant are formed in the outer ball raceway surface 21 of the inner bearing ring 2, and

grooves

241, 242 are formed on left and right side surfaces 221, 222 in an axial direction thereof.

The outer bearing ring 1 forms a three-stage step with L-shaped cross sections which are divided into a left outer ring 11 and a right outer ring 12 which are in cover ring shapes; the outer diameter of the outer ring on one side of the combined left and right outer bearing rings 11 and 12 is smaller than that of the outer ring on the other side, or the outer diameters of the outer rings on both sides of the combined left and right outer bearing rings 11 and 12 are the same; the first steps 121, 122 of the three steps of the left and right outer bearing rings 11, 12 are combined to form a toroidal-spherical space having an inner cavity with an inner diameter size larger than the outer diameter size of the inner bearing ring 2, and the first steps 121, 122 are formed as toroidal-spherical inner cavity raceway surfaces 123, 124 in the toroidal-spherical space thereof; the second steps 131, 132 of the left and right outer bearing rings 11, 12 are formed into inner spherical shapes having the same inner diameter dimension as the outer diameter dimension of the inner bearing ring 2, and the second steps 131, 132 are formed into inner spherical raceway surfaces 133, 134 at the inner spherical end portions thereof; the annular limiting parts 145 and 146 on the inner side walls of the third steps 141 and 142 of the left and right hemispherical outer rings 11 and 12 of the outer bearing ring 1 are provided with axial linear concave-convex parts 151, 153, 152 and 154; the axial outer side surfaces of the third steps 141 and 142 are formed into circular ring-shaped planes 143 and 144, eight staggered bolt counterbores 5 are arranged on the peripheries of the circular ring-shaped planes 143 and 144, and extend from the circular ring-shaped planes 143 and 144 to opposite surfaces through the axial side walls 125 and 126 of the first steps 121 and 122; the third steps 141, 142 of the left and right hemispherical outer rings 11, 12 of the outer bearing ring 1, the annular limit parts 145, 146 and the second and first steps 131, 132, 121, 122 are spherically formed into upper and lower raceways of a stepped spherical surface connecting the spherical inner cavity raceway surfaces 122, 124 and the spherical inner raceway surfaces 132, 134 integrally, and the inner side wall annular limit parts 145, 146 are formed into axial concave-convex parts 151, 153, 152, 154; the axial left and right end faces 125, 126 of the combination of the left outer ring 11 and the right outer ring 12 of the outer bearing ring 1 are on the radial spherical center ray, the outer bearing ring 1 and the outer ball raceway surface 21 of the inner bearing ring 2 are arranged on the same spherical center through the toroidal cavity raceway surfaces 123, 124, and the plural rows of first and third balls 31, 32, 321, 322 are arranged between the outer ball raceway surface 21 and the toroidal cavity raceway surfaces 123, 124 of the outer bearing ring 1 so as to be rollably arranged in a state of being axially distributed and spaced by the retainers 41, 42, 43, 44, and are arranged between the grooves 241, 242 of the axial left and right side faces 221, 222 and the linear concave-convex portions 151, 153, 152, 154 of the inner side wall annular stopper portions 145, 146.

second steps

A space for accommodating the plurality of rows of

first balls

ball rolling surfaces

123 and 124 and the outer ball rolling surface 21 can accommodate a plurality of rows of

first balls

31 and 32 and enable the first balls to roll in two spherical raceways, in order to keep the relative positions of the plurality of rows of

first balls

31 and 32,

retainers

41 and 42 with radial ball ring surfaces are added, the

retainers

41 and 42 are matched with the left outer bearing ring 11 and the right outer bearing ring 12 to enable the axial ring spherical surfaces of the two rows of

first balls

31 and 32 to be uniformly distributed at intervals, and the relative positions of the balls of the

first balls

31 and 32 in each row can be ensured not to change in the rolling process. The

retainers

balls

31 and 32.

The distance of the side walls 135 and 136 of the opposite second steps 131 and 132 of the left outer ring 11 and the right outer ring 12 of the outer bearing ring 1 is set to enable two rows of first balls 31 and 32 to freely rotate in the inner ball cavity raceway surfaces 123 and 124, when the angle deflection is large, the two rows of first balls 31 and 32 can be in contact with the axial side walls 135 and 136 through the retainers 41 and 42, meanwhile, the pockets of the retainers 41 and 42 are deviated to the inner bearing ring 2 relative to the two rows of first balls 31 and 32, and when the rotation angle of the inner bearing ring 2 of the swing bearing is deviated to the left and right rows of first balls 31 and 32, the pockets of the retainers 41 and 42 can be matched with the outer bearing ring 1 to keep the relative position of each ball unchanged; further, the distance from the inner side wall annular limiting parts 145 and 146 of the third steps 141 and 142 of the left and right outer rings 11 and 12 of the outer bearing ring 1 to the axial left and right side surfaces 221 and 222 of the inner bearing ring 2 can accommodate two rows of third balls 321 and 322, the distance from the opposite linear concave-convex parts 151, 153, 152 and 154 in the annular limiting parts 145 and 146 to the channels 241 and 242 of the axial left and right side surfaces 221 and 222 of the inner ring 2 is further arranged, and four balls formed into a cross shape by the two rows of third balls 321 and 322 are held by four pockets of the axial retainers 43 and 44; the diameter of each ball of the left and right rows of third balls 321 and 322 is equal to the distance from the linear concave-convex parts 151, 153, 152 and 154 in the left and right inner side wall annular limiting parts 145 and 146 to the raceway grooves 241 and 242 of the left and right end surfaces 221 and 222 in the axial direction, and the two rows of third balls 321 and 322 roll in the annular limiting parts 145 and 146, the concave-convex parts 151, 153, 152 and 154 and the channels 241 and 242; the two rows of third balls 321 and 322 shown in fig. 14 roll on the linear concave-convex portions 151, 153, 152 and 154, further restricting the inner ring 2 of the rocking bearing to rotate and drive the outer ring 1 to rock, when the four cross-shaped balls of the left and right rows of third balls 321 and 322 roll once on the annular limiting portions 145 and 146 of the outer ring 1, the four cross-shaped balls reach the concave-convex portions 151, 153, 152 and 154, and drive the outer ring 1 to rock four times, the rocking frequency is high and the stroke speed is strong, and fig. 14 shows that the relative inclination between the axial center lines of the inner and outer rings 2 and 1 of the rocking bearing is an angle B.

The oscillating bearing device is assembled in an operable sequence: the right outer ring 12 with the small outer diameter of the outer bearing ring 1 is horizontally placed on a workbench, two opposite balls of one row of third balls 322 on the right side in the axial direction are assembled on concave-

convex parts

152 and 154 of a third step 142 annular limiting part 146 of the right outer ring 12 with the small outer diameter in the second step, one row of first balls 32 in a rolling surface 124 of an annular inner cavity of the ring ball are assembled in the third step, the inner bearing ring 2 is assembled in two rows of third and

first balls

322 and 32 in the right outer ring 12 in the fourth step, a T-shaped round rod penetrates through a mandrel of the inner bearing ring 2 in the fifth step, the assembled half of the right outer ring 12, the two rows of third and

first balls

322 and 32 and the inner ring 2 are reversely buckled in the other half of the assembled left outer ring 11 with the large outer diameter and the two rows of third and

first balls

321 and 31 assemblies, and finally the left and right outer rings 11 and 12 are connected through bolts 51 for pre-tightening and fixing.

There are two types of movement of the oscillating bearing according to different designs: first, rolling → rolling plus sliding, fig. 13 to 15 are assembled in the above form, the diameters of the in-ring ball raceway surfaces 133, 134 of the opposing

second steps

first balls

31, 32 of each left and right row of the radial extension line on the center of the sphere are arranged in a left and right direction in an axial direction, and the diameter of each ball of the

first balls

31, 32 of each left and right row is larger than the distance from the inner cavity raceway surfaces 123, 124 to the outer ball raceway surface 21, and is larger than the data range value of 0.003mm to 0.005 mm. Then, according to the axial clearance between the left and right outer bearing rings 11, 12, the fixing screw 51 applies a pre-tightening force to adjust the moment of the elastic pad 6, so that the purpose of accurately adjusting the clearance between the left and right rows of

first balls

31, 32 and the inner

ball rolling surfaces

123, 124 of the ring ball and the outer ball rolling surface 21 can be achieved. At outer race 1, when multiseriate rolling element 3 and the 2 sports fatigue wearing and tearing of inner race, the diameter of three is changing, the external diameter of the left outer lane 11 of the hemisphere outer lane of the 1 combination of outer race is greater than the external diameter of right outer lane 12, through the flexible combination of hemisphere outer lane, the hemisphere outer lane 11 and the bearing box interference fit that the external diameter is big, the automatic flexible pretension of hemisphere outer lane 12 that the external diameter is little, 5 overhead bullet pads 6 of fixing bolt have an elasticity to make outer race 1, multiseriate rolling element 3 and inner race 2 are fixed together all the time. Through the adjustment, the original spherical contact is changed into the rolling contact of the multiple rows of rolling bodies 3, and on one hand, the gaps between the multiple rows of

first balls

31 and 32 and the inner bearing ring 2 and the gaps between the multiple rows of

first balls

31 and 32 and the left outer ring 11 and the right outer ring 12 can be adjusted through the automatic adjustment of the torque of the pretightening force of the elastic pad 6 of the fixing screw 51. After the rolling elements 3 in the left and right rows in the axial direction wear due to fatigue, the inner ball raceway surfaces 133 and 134 and the outer ball raceway surface 21 make sliding motion. On the other hand, the original bearing rolling friction is changed into the rolling and sliding friction of the oscillating bearing. Through the change, firstly, the gap is accurately controlled, and meanwhile, a certain pretightening force can be applied to achieve the aim of no gap, so that the movement precision is improved; and secondly, rolling friction and sliding friction are combined, so that the coefficient of the rolling friction can be effectively reduced, the service life of the bearing is prolonged, and particularly the lubricating service life under the condition of heavy load and high speed is prolonged.

Secondly, the simultaneous sliding and rolling movements, fig. 13 to 15, are assembled as above, and it is also possible to provide that the diameters of the globoid inner and outer rolling

surfaces

123, 124 of the outer bearing ring 1 and the outer ball rolling surface 21 of the inner bearing ring 2 are the same as the diameters of the globoid inner and outer diameters of the distributed two rows of the first balls 31, 32 (the diameter of each ball of the two rows of the

balls

31, 32 is equal to the distance from the globoid inner rolling surfaces 123, 124 to the outer ball rolling surface 21). The diameters of the inner ball raceway surfaces 133 and 134 of the second step of the outer bearing ring 1 and the outer ball raceway surface 21 of the inner bearing ring 2 are the same, the outer bearing ring 1, the left and right rows of

first balls

bodies

31, 32, 321 and 322 and the inner bearing ring 2 are fixed to slide and roll integrally and move simultaneously.

Third embodiment

As shown in fig. 16 to 18, the present invention relates to a rocking bearing.

The oscillating bearing is applied to general machinery, such as the fields of underground drilling, plunger pumps, internal combustion engines, electric tools, wind power equipment, helicopter rotor wing mechanisms and the like.

The rocking bearing according to the third embodiment of the bearing shown in fig. 16 to 18 includes an outer bearing ring 1 and an inner bearing ring 2 coaxial with the outer bearing ring 1 and having a spherical center, and the rolling elements 3 may be arranged in a plurality of rows on the raceway surfaces 123 and 124 of the inner spherical cavity so that at least two rows of

first balls

31 and 32 are arranged on the left and right sides across the radial line of the spherical center in the radial direction, and two rows of

fourth slope balls

341 and 342 are arranged on the left and right sides in the

annular stopper portions

145 and 146 of the

third steps

141 and 142 and the

retainers

41, 42, 45, and 46 are arranged on the axial direction.

The inner bearing ring 2 is formed in a cap ring shape, an outer ball raceway surface 21 is formed on an outer spherical surface thereof, a plurality of blind holes for retaining a solid lubricant are formed in the outer ball raceway surface 21 of the inner bearing ring 2, center axes of left and right side surfaces 231, 232 in an axial direction thereof are disposed obliquely with respect to an axis of the transmission shaft, and left and right inclined side surfaces 231, 232 in the axial direction of the inner bearing ring 2 are disposed in parallel with each other.

The outer bearing ring 1 forms a three-stage step with L-shaped cross sections which are divided into a left outer ring 11 and a right outer ring 12 which are in cover ring shapes; the outer diameter of the outer ring on one side of the combined left and right outer bearing rings 11 and 12 is smaller than that of the outer ring on the other side, or the outer diameters of the outer rings on both sides of the combined left and right outer bearing rings 11 and 12 are the same; the first steps 121, 122 of the three steps of the left and right outer bearing rings 11, 12 are combined to form a toroidal-spherical space having an inner cavity with an inner diameter size larger than the outer diameter size of the inner bearing ring 2, and the first steps 121, 122 are formed as toroidal-spherical inner cavity raceway surfaces 123, 124 in the toroidal-spherical space thereof; the second steps 131, 132 of the left and right outer bearing rings 11, 12 are formed into inner spherical shapes having the same inner diameter dimension as the outer diameter dimension of the inner bearing ring 2, and the second steps 131, 132 are formed into inner spherical raceway surfaces 133, 134 at the inner spherical end portions thereof; inner side wall annular limiting parts 145 and 146 of third steps 141 and 142 of left and right hemispherical outer rings 11 and 12 of the outer bearing ring 1 are provided with raceway grooves 147 and 148; the third steps 141, 142 of the left and right hemispherical outer rings 11, 12 of the outer bearing ring 1 and the second and first steps 131, 132, 121, 122 are spherical surfaces which form an upper and a lower raceways of a stepped spherical surface connecting the annular inner cavity raceway surfaces 122, 124 and the annular inner raceway surfaces 132, 134 into a whole, and the inner side wall annular limiting parts 145, 146 form axial raceway grooves 147, 148; the axial left and right end faces 125, 126 of the combination of the left outer ring 11 and the right outer ring 12 of the outer bearing ring 1 are on the radial spherical center ray, the outer bearing ring 1 and the outer ball raceway surface 21 of the inner bearing ring 2 are arranged on the same spherical center with the annular inner cavity raceway surfaces 123, 124 interposed therebetween, and the plural rows of first balls 31, 32 and fourth slope balls 341, 342 are arranged rollably between the outer ball raceway surface 21 and the annular inner cavity raceway surfaces 123, 124 of the outer bearing ring 1, and between the axial left and right slope side faces 231, 232 and the grooves 147, 148 in a state of being axially distributed and held at intervals by the retainers 41, 42, 45, 46.

second steps

A space for accommodating the plurality of rows of

first balls

ball rolling surfaces

first balls

31 and 32,

retainers

41 and 42 with radial ball ring surfaces are added, the

retainers

first balls

balls

31 and 32 in each row can be ensured not to change in the rolling process. The

retainers

balls

31 and 32.

The distance of the side walls 135 and 136 of the opposite second steps 131 and 132 of the left outer ring 11 and the right outer ring 12 of the outer bearing ring 1 is set to enable two rows of first balls 31 and 32 to freely rotate in the inner ball cavity raceway surfaces 123 and 124, when the angle deflection is large, the two rows of first balls 31 and 32 can be in contact with the axial side walls 135 and 136 through the retainers 41 and 42, meanwhile, the pockets of the retainers 41 and 42 are deviated to the inner bearing ring 2 relative to the two rows of first balls 31 and 32, and when the rotation angle of the inner bearing ring 2 of the swing bearing is deviated to the left and right rows of first balls 31 and 32, the pockets of the retainers 41 and 42 can be matched with the outer bearing ring 1 to keep the relative position of each ball unchanged; further, the distance from the third step 141, 142 of the left and right outer rings 11, 12 of the outer bearing ring 1 to the inner wall annular limiting parts 145, 146 to the axial left and right inclined side surfaces 231, 232 of the inner bearing ring 2 can accommodate two rows of fourth inclined balls 341, 342, the two rows of fourth inclined balls 341, 342 arranged from the annular limiting parts 145, 146 to the axial left and right inclined side surfaces 231, 232 of the inner ring 2 are formed in such a way that the fourth inclined balls 341, 342 are distributed at intervals from the large diameter balls 331, 334 to the small diameter balls 332, 333, and the balls of different diameters of the fourth inclined balls 341, 342 are opposite to each other in pairs on a straight line and are held by the pockets of different sizes of the axial retainers 45, 46; the large diameter ball 331 of the left row of balls 341 of the fourth annular ramp balls 341, 342 is disposed opposite to the small diameter ball 332 of the right row of balls 342, and the axial diameter of each ball of the left and right rows of fourth annular ramp balls 341, 342 is equal to the distance from the raceway grooves 147, 148 of the left and right inner side wall annular stoppers 145, 146 to the left and right inclined side surfaces 231, 232 in the axial direction; the curvature of the curves of the raceway grooves 147, 148 formed by the inner side wall annular limiting parts 145, 146 of the left and right hemispherical outer rings 11, 12 of the outer bearing ring 1 and the third steps 141, 142 is further arranged to be configured by large-diameter balls 331, 334; the two rows of the fourth annular ramp balls 341 and 342 shown in fig. 18 roll between the inner and outer raceways 231, 232, 147, and 148, and the slope of the fourth annular ramp balls 341 and 342 is 3 to 15 degrees; the fourth ring-shaped ramp balls 341 and 342 of fig. 18 roll 180 degrees relative to the left and right inclined side surfaces 231 and 232 of the axial direction, so that the inner ring 2 of the rocking bearing is further limited to rotate to drive the outer ring 1 to linearly and reciprocally rock, and the relative inclination between the axial lines of the inner ring 2 and the outer ring 1 of the rocking bearing shown in fig. 18 is an angle a.

The rocking bearing device is assembled in an operable order that the right outer ring 12 of the outer race 1 having a small outer diameter is laid on a table, the right one-row fourth slope ball 342 in the axial direction of the second step is placed in the raceway groove 148 of the third step 142 of the right outer ring 12 having a small outer diameter, the one-row first ball 32 in the raceway surface 124 of the inner cavity of the spherical ring is assembled in the third step, the right slope 232 of the inner race 2 is placed in the two rows of balls 342, 32 in the right outer ring 12 in the fourth step, the slope of the right slope 232 is correspondingly placed on the slope of the slope ball 342, the fifth step is to pass a T-shaped rod through the core shaft of the inner race 2, and the half of the assembly of the right outer ring 12, the two rows of balls 342, 32 and the inner race 2 is reversely buckled in the other half of the assembly of the left outer ring 11 and the two rows of balls 341, 31 having a large outer diameter, and finally the left and right outer rings 11, b are connected by bolts 51, 12 are pre-tightened and fixed.

There are two types of movement according to different designs of the oscillating bearing device: first, rolling → rolling plus sliding, fig. 16 to 18 are assembled in the above form, the diameters of the in-ring ball raceway surfaces 133, 134 of the opposing

second steps

first balls

31, 32 is larger than the distance from the rolling

surface

balls

31, 32 and the inner

ball rolling surfaces

123, 124 of the ring ball and the outer ball rolling surface 21 can be achieved. When the outer bearing ring 1, the multi-column rolling bodies 3 and the inner bearing ring 2 are in fatigue wear in motion, the diameters of the outer bearing ring 1, the multi-column rolling bodies 3 and the inner bearing ring 2 are changed, the outer diameter of a left outer ring 11 of a hemisphere outer ring combined by the outer bearing ring 1 is slightly larger than the outer diameter of a right outer ring 12, the hemisphere outer ring 11 with the large outer diameter is in interference fit with a bearing box through flexible combination of the hemisphere outer ring, the hemisphere outer ring 12 with the small outer diameter is automatically and flexibly pre-tightened, and an elastic pad 6 on a fixing bolt 5 head has elastic force to enable the outer bearing ring 1, the multi-column rolling balls 3 and the inner bearing ring 2 to be fixed together all the time. Through the adjustment, the original spherical contact is changed into the rolling contact of the multiple rows of rolling bodies 3, and on one hand, the gaps between the multiple rows of balls 3 and the inner bearing ring 2 and the gaps between the multiple rows of balls 3 and the left outer ring 11 and the right outer ring 12 can be adjusted through the automatic adjustment of the torque of the pretightening force of the elastic pad 6 of the fixing screw 51. After the rolling elements 3 in the left and right rows in the axial direction wear due to fatigue, the inner ball raceway surfaces 133 and 134 and the outer ball raceway surface 21 make sliding motion. On the other hand, the original bearing rolling friction is changed into the rolling and sliding friction of the oscillating bearing. Through the change, firstly, the gap is accurately controlled, and meanwhile, a certain pretightening force can be applied to achieve the aim of no gap, so that the movement precision is improved; and secondly, rolling friction and sliding friction are combined, so that the coefficient of the rolling friction can be effectively reduced, the service life of the bearing is prolonged, and particularly the lubricating service life under the condition of heavy load and high speed is prolonged.

Secondly, sliding and rolling are simultaneously moved, fig. 16 to 18 are assembled as above, and the diameters of the spherical inner cavity raceway surfaces 123 and 124 of the outer bearing ring 1 and the outer ball raceway surface 21 of the inner bearing ring 2 may be set to be the same as the spherical inner and outer diameters of the distributed left and right rows of first balls 31 and 32 (the diameter of each ball of the left and right rows of

first balls

31 and 32 and the inner bearing ring 2 are concentric, and a pretightening force is applied to eight opposite fixing bolts 51 of the left and right outer bearing rings 11 and 12, so that the elastic pad 6 has a certain moment, and the outer bearing ring 1, the multiple rows of

balls

31 and 32, 341 and 342 and the inner bearing ring 2 are fixed to slide integrally and roll simultaneously.

Fourth embodiment

As shown in fig. 19 to 24, the present invention relates to a rocking bearing.

The oscillating bearing is applied to general machinery, such as rolling mills, underground drilling, crushing and grinding equipment, plunger pumps, internal combustion engines, electric tools, wind power equipment, helicopter rotor wing mechanisms and other fields.

Reciprocating tools that are currently driven by motors, such as hammer drills, saber saws, and the like, are typically driven by a motor having a rotating output shaft. The rotary motion is converted into a reciprocating motion of a working shaft for moving a drill bit or the like in a reciprocating manner. Various methods have been developed to convert rotational motion into reciprocating motion. The usual approach is to incorporate a wobble bearing drive.

The rocking bearing according to the fourth embodiment of the bearing shown in fig. 19 to 24 includes an outer bearing ring 1 and an inner bearing ring 2 coaxial with the outer bearing ring 1 and having a spherical center, and the rolling elements 3 may be formed in a plurality of rows such that at least two rows of

first balls

31 and 32 are arranged on the right and left sides across a radial line of the spherical center in the radial direction on the rolling

surface

123 and 124 of the inner spherical cavity, and two rows of second cylindrical rollers 351 and 352 on the right and left sides of the

annular stopper portions

145 and 146 of the

third steps

141 and 142 are arranged in the axial direction with respect to each other, and the

retainers

41, 42, 47, and 48.

The inner bearing ring 2 is formed in an annular shape, an outer spherical raceway surface 21 is formed on an outer spherical surface thereof, a plurality of blind holes for retaining a solid lubricant are formed in the outer spherical raceway surface 21 of the inner bearing ring 2, center axes of left and right axial side surfaces 231, 232 thereof are disposed obliquely with respect to an axis of the transmission shaft, and left and right axial oblique side surfaces 231, 232 of the inner bearing ring 2 are disposed in parallel with each other.

The outer bearing ring 1 forms a three-stage step with L-shaped cross sections which are divided into a left outer ring 11 and a right outer ring 12 which are in cover ring shapes; the outer diameter of the outer ring on one side of the combined left and right outer bearing rings 11 and 12 is smaller than that of the outer ring on the other side, or the outer diameters of the outer rings on both sides of the combined left and right outer bearing rings 11 and 12 are the same; the first steps 121, 122 of the three steps of the left and right outer bearing rings 11, 12 are combined to form a toroidal-spherical space having an inner cavity with an inner diameter size larger than the outer diameter size of the inner bearing ring 2, and the first steps 121, 122 are formed as toroidal-spherical inner cavity raceway surfaces 123, 124 in the toroidal-spherical space thereof; the second steps 131, 132 of the left and right outer bearing rings 11, 12 are formed into inner spherical shapes having the same inner diameter dimension as the outer diameter dimension of the inner bearing ring 2, and the second steps 131, 132 are formed into inner spherical raceway surfaces 133, 134 at the inner spherical end portions thereof; axial inner side walls of third steps 141 and 142 of left and right hemispherical outer rings 11 and 12 of an outer bearing ring 1 are formed into annular limiting parts 145 and 146 to be provided with plane raceways, axial outer side faces of the third steps 141 and 142 are formed into annular planes 143 and 144, the peripheries of the annular planes 143 and 144 are provided with eight staggered bolt counter bores 5, and the annular planes 143 and 144 pass through the axial side walls 125 and 126 of the first steps 121 and 122 to opposite faces; the third steps 141, 142 and the second and first steps 131, 132, 121, 122 of the left and right hemispherical outer rings 11, 12 of the outer bearing ring 1 form a cover ring-shaped step which is connected into a whole, the spherical inner cavity raceway surfaces 123, 124 and the spherical inner raceway surfaces 133, 134 are spherical upper and lower raceways, and the axial inner side walls of the annular limiting parts 145, 146 are provided with plane raceways; the axial left and right end faces 125, 126 of the first steps 121, 122 of the combination of the left outer ring 11 and the right outer ring 12 of the outer bearing ring 1 are on or offset from the spherical center ray in the radial direction; the outer bearing ring 1 and the outer ball raceway surface 21 of the inner bearing ring 2 are arranged on the same sphere center through the ring ball inner cavity raceway surfaces 123 and 124; the first balls 31, 32 and the second cylindrical rollers 351, 352 in two rows are rollably arranged between the outer ball raceway surface 21 and the toroidal inner cavity raceway surfaces 123, 124 of the outer bearing ring 1, and between the axially leftward and rightward inclined side surfaces 231, 232 and the annular stopper portions 145, 146 in a state of being axially spaced apart by the retainers 41, 42, 47, 48.

window type cages

47 and 48, the sections of the annular

window type cages

plane rolling surfaces

145 and 146 and the radial inner diameter end parts of the

third step

window type cages

47 and 48 are provided with parallel arc-shaped surfaces; the left and right sides of the inner diameter surface of the T-shaped upper part of the annular

window type retainers

47 and 48 extending axially can be sleeved with rubber sealing rings.

second steps

A space for accommodating the plurality of rows of

first balls

ball rolling surfaces

first balls

31 and 32,

retainers

41 and 42 of a radial annular spherical surface are added, the

retainers

first balls

balls

31 and 32 in each row can be ensured not to change in the rolling process; the

retainers

balls

31 and 32.

The distance of the side walls 135 and 136 of the opposite second steps 131 and 132 of the left outer ring 11 and the right outer ring 12 of the outer bearing ring 1 is set, so that two rows of first balls 31 and 32 can freely rotate in the rolling surfaces 123 and 124 of the inner ball cavity, when the angular deflection is relatively large, the two rows of balls 31 and 32 can be in contact with the axial side walls 135 and 136 of the retainers 41 and 42, meanwhile, the pockets of the retainers 41 and 42 are deviated from the inner bearing ring 2 relative to the two rows of balls 31 and 32, and when the rotating angle of the inner bearing ring 2 of the combined bearing is deviated from the two rows of balls 31 and 32, the pockets of the retainers 41 and 42 can be matched with the outer bearing ring 1 to keep the relative position of each ball unchanged; further, the distance from the inner side wall annular limiting parts 145 and 146 of the third steps 141 and 142 of the left and right outer rings 11 and 12 of the outer bearing ring 1 to the axial left and right inclined side surfaces 231 and 232 of the inner bearing ring 2 can accommodate two rows of second cylindrical rollers 351 and 352, the diameter of each roller of the left and right rows of second cylindrical rollers 351 and 352 is equal to the distance from the left and right inner side wall annular limiting parts 145 and 146 to the axial left and right inclined side surfaces 231 and 232, and the rollers roll on the two plane raceways 145, 146, 231 and 232, as shown in fig. 20, when the inner ring 2 rotates to drive the outer ring 1 to do linear torsional reciprocating motion, the axial lines of the inner and outer rings 2 and 1 of the wobble bearing of the fourth embodiment are further limited to swing at an angle K; if the inner ring 2 is fixed and the outer ring 1 rolls on the road surface, the bearing can be used in a wheel bearing, and the left and right opposite wheels move in a splayed (trapezoidal) skimming manner.

The oscillating bearing is assembled according to the operable sequence that the right outer ring 12 with small outer diameter of the outer bearing ring 1 is flatly placed on a workbench, the right column of second cylindrical rollers 352 on the right side of the axial direction of the second step are placed in a plane raceway of the annular limiting part 146 on the inner side wall of the third step 142 of the right outer ring 12 with small outer diameter, the right column of first balls 32 in the inner cavity raceway surface 124 of the third step are assembled, the inner bearing ring 2 of the fourth step is placed in two columns of rolling bodies 352 and 32 in the right outer ring 12, the fifth step is that a T-shaped round rod penetrates through a mandrel of the inner bearing ring 2, the assembled half of the right outer ring 12, two columns of rolling bodies 352 and 32 and the assembly of the inner ring 2 are reversely buckled in the other half of the assembled left outer ring 11 with large outer diameter and two columns of rolling bodies 351 and 31, and finally the left and right outer rings 11 and 12 are connected and fixed in a pre-tightening way by bolts 51.

There are two kinds of movement modes according to different combined bearings: first, rolling → rolling plus sliding, fig. 19 to 24 are assembled in the above form, the diameters of the in-ring ball raceway surfaces 133, 134 of the opposing

second steps

first balls

31, 32 is larger than the distance from the rolling

surface

first balls

31, 32 and the inner

ball rolling surfaces

Secondly, the simultaneous sliding and rolling movements, fig. 19 to 24, are assembled as above, and it is also possible to provide that the diameters of the spherical inner raceway surfaces 123, 124 of the outer bearing ring 1 and the outer spherical raceway surface 21 of the inner bearing ring 2 are the same as the spherical inner and outer diameters of the distributed right and left rows of first balls 31, 32 (the diameter of each ball of the right and left rows of

first balls

31, 32 is equal to the distance from the inner raceway surfaces 123, 124 to the outer spherical raceway surface 21). The diameters of the inner ball raceway surfaces 133 and 134 of the second step of the outer bearing ring 1 and the outer ball raceway surface 21 of the inner bearing ring 2 are the same, the outer bearing ring 1, the left and right rows of

first balls

bodies

Fifth embodiment

A fifth embodiment is shown in fig. 25-26-27 of the axial cage for cylindrical rollers after disassembly of the combination bearing and the fourth embodiment rocking bearing according to the first embodiment with one roller installed.

window type cages

47 and 48, the sections of the annular

window type cages

plane rolling surfaces

145 and 146 and the radial inner diameter end parts of the

third step

window type cages

window type retainers

47 and 48, which axially extends.

Sixth embodiment

Fig. 28 and 29 show a rocking bearing designed according to the present invention.

Fig. 28 to 29 show the same features of the second embodiment as the rocking bearing of the sixth embodiment is designed differently, and

linear irregularities

261, 263, 262, 264 of left and right axial side surfaces 221, 222 of the inner ring 2 are provided.

Can be applied to general machines.

It can be seen from the figures that the same features of the second embodiment are incorporated into the sixth embodiment, which can be combined in a variable manner, and will not be described again here.

Emphasis on description of fig. 28 fig. 29 distinguishing features: the annular stopper portions 145, 146 of the third steps 141, 142 of the left and right outer rings 11, 12 are provided with grooves 147, 148, the axially left and right side surfaces 221, 222 of the inner bearing ring 2 are provided with axially convex and concave portions in a linear mating manner, the convex portion 263 of the left side surface 221 of the inner ring 2 is disposed in relation to the concave portion 264 of the right side surface 222 of the inner ring 2, the concave portion 261 of the left side surface 221 of the inner ring 2 is disposed in relation to the convex portion 262 of the right side surface 222 of the inner ring 2, the linear convex and concave portions 263, 261 of the left side surface 221 of the inner ring 2 are disposed in relation to the linear concave and convex portions 264, 262 of the right side surface 222 of the inner ring 2, the axially left and right side surfaces 221, 261, 263, 262 of the inner bearing ring 2 are disposed in relation to the linear concave and convex portions 264 of the right side surface 222 of the inner bearing ring 2, the curvatures of the axially left and right side surfaces 221, 261, 263, 262 of the inner bearing ring 2 are the same, 262, 264 are disposed in relation to the axially left and right side surfaces of the outer rings 11, 12, the third steps 141, 142 of the annular stopper portions 145, 148, 142 in relation to the outer ring 1, 146 channels 147, 148 are arranged in parallel;

the third step 141, 142 annular limiting part 145, 146 channel 147, 148 of the left and right outer rings 11, 12 is arranged to the distance (space) from the left and right side surfaces 221, 222 of the inner bearing ring 2 to the annular limiting part 145, 146 channel 147, 148 of the left and right outer rings 11, 12 to the linear convex-concave part 261, 263, 262, 264, the third rolling element 321, 322 is a left and right two rows of third balls 321, 322, each row of the third balls 321, 322 is a cross shape formed by four balls surrounded by four pockets of the axial cage, each diameter of the four balls 321, 322 of the cross shape of the two rows is the same, the radius of the balls of the third balls 321, 322 of each row is slightly smaller than the curvature of the cross-section curves of the convex part, the concave part 262, 263, 261, 264, the two rows of the cross shape third balls 321, 322 can be guided to the left and right side surfaces 221, 222 and the linear convex-concave part 261, 263 of the inner ring 2, the 262, the outer ring 1 annular limiting part 145, the channel 146, 147, 148.

Fig. 29 shows that the two rows of third balls 321 and 322 of the rocking bearing of the sixth embodiment of the present invention roll on the straight concave-convex portions 261, 263, 262, 264 of the left and right side surfaces 221 and 222 of the inner ring 2 according to fig. 28, and as shown in fig. 29, when the outer ring 1 rotates, the inner ring 2 is driven to rock, assuming that the axial line of the outer ring 1 is parallel to the horizontal direction, the X axis of the inner ring 2 perpendicular to the horizontal direction will rock once from the N direction to the M direction at an angle, when the two rows of third balls 321 and 322 roll on the left and right side surfaces 221 and 222 of the inner ring 2 to leave the straight concave-convex portions 261, 263, 262, 264, the inner ring 2 will return to the right direction, when the four crossed balls of the left and right rows of third balls 321 and 322 rotate once on the axial side surfaces 221 and 222 of the inner ring 2, the four crossed balls reach the concave-convex portions 261, 263, 262, 264 four times, the inner ring 2 will be driven to rock four times, the rocking frequency is high and the stroke is fast and violent, can be used on a curve saw and an electric nailing gun, and the view is omitted.

Fig. 29 shows that the two rows of

third balls

321 and 322 of the rocking bearing according to the sixth embodiment of the present invention according to fig. 28 roll on the linear concave-

convex portions

261, 263, 262, and 264 of the left and right

axial surfaces

221 and 222 of the inner ring 2, and drive the outer ring 1 to rock regularly at different points in the circumferential direction when the inner ring 2 rotates, and is applied to a general-purpose machine.

Seventh embodiment

Fig. 30 is a perspective view of a swing bearing device 8 according to a seventh embodiment of the present invention, showing a swing arm arranged in the swing bearing device 8, according to the second, third, and fourth embodiments, showing a reciprocating swing bearing device 8 according to the present invention.

According to fig. 30, a sleeve 91 of a swing arm 9 of a reciprocating swing bearing device 8 as a seventh embodiment of a bearing is sleeved on a left outer ring 11 with a large outer diameter of the swing bearing, the swing arm 9 is fixed by a bolt 93, a round bar 92 is arranged at an end of an extension arm of the swing arm 9, the round bar 93 on the swing arm 9 rotates relative to a reciprocating swing direction, and the inner ring 2 drives the outer ring 1 to swing.

The invention has not been described in detail in part of the common general knowledge of those skilled in the art.

Claims

1. A composite bearing, characterized by: the rolling bearing comprises an outer bearing ring (1), an inner bearing ring (2), a plurality of rows of rolling bodies (3), retainers (41-48) and fixing bolts (51), wherein the associated parts of the outer bearing ring (1) and the inner bearing ring (2) are spherical surfaces;

2. The combination bearing of claim 1, wherein:

3. The combination bearing of claim 2, wherein:

4. The combination bearing of claim 3, wherein:

5. A composite bearing comprising a composite bearing according to any one of the preceding claims, wherein:

6. The combination bearing of claim 5, wherein:

7. A rocking bearing comprising a combination bearing according to any one of claims 1 to 5, wherein:

8. A rocking bearing comprising a combination bearing according to any one of claims 1 to 6, wherein:

9. A rocking bearing comprising a combination bearing according to any one of claims 1 to 5, wherein:

10. Oscillating bearing device (8) comprising an oscillating bearing according to any of claims 7 to 9, characterized in that: