CN115638186A - Stable, passive and active combined bearing and/or transmission device and retainer, and equipment machine using various transmission devices - Google Patents
Stable, passive and active combined bearing and/or transmission device and retainer, and equipment machine using various transmission devices Download PDFInfo
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- CN115638186A CN115638186A CN202211313259.2A CN202211313259A CN115638186A CN 115638186 A CN115638186 A CN 115638186A CN 202211313259 A CN202211313259 A CN 202211313259A CN 115638186 A CN115638186 A CN 115638186A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
- F16C25/08—Ball or roller bearings self-adjusting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/38—Ball cages
- F16C33/40—Ball cages for multiple rows of balls
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Friction Gearing (AREA)
Abstract
A stable, passive and active combined bearing and/or transmission device (1, 3, 7 a) and a retainer (500), and an equipment machine using various transmission devices; the superposition and the separation of the spherical raceways (905, 906, 909a,909 b) of the inner ring (120, 380, 720, 620) and the outer ring (100, 300, 600, 700) of the device correspond to the transmission raceway surfaces in the axial direction of the inner ring and the outer ring, and are provided with motion control modes for different rolling elements (141, 142, 351,352, 741,742, 680), the inner ring forms a ring-shaped radial spherical raceway (909, 909a,909 b) and a first and a second raceway (121, 122, 381,382, 722, 623, 624) in the axial direction and/or forms a split inner ring (621, 622) which is axially opposite, and the outer ring forms an inner raceway of the first and the second split outer rings (101, 102, 301,302, 701,702, 601, 602); the play of each element in the device in the axial direction and the radial direction is automatically flexibly adjusted to keep stable and accurate movement.
Description
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.: 202111007956.0, division filing date: 30.08.2021, bearing, precession bearing gyro and active gyro stabilizer using precession bearing gyro "
Technical Field
The invention relates to the field of bearings. In a first aspect, the invention provides a combined bearing and/or transmission device, which is characterized in that spherical raceways of at least one or at least one of an inner ring and an outer ring are superposed and separated, correspond to raceways in the axial directions of the inner ring and the outer ring, and are matched with different rolling bodies and/or control motion modes of transmission elements; the inner ring forms an annular radial spherical raceway and a first raceway, a second raceway and/or an inner ring in the axial direction form an axial split type; the outer ring forms a split type variation design of the contact morphology of the inner raceways of the first outer ring and the second outer ring, the spherical raceway spaces of the inner ring and the outer ring, which are radially separated, in the middle of the bearing are point-contact rolling motion of a plurality of angular contact ball rows maintained by axially distributed retainers, the spherical raceways of the inner ring and the outer ring, which are positioned at two sides of the middle of the bearing, are in surface contact sliding motion, and the rolling bodies in the axial direction and/or the raceways of the transmission elements, which are matched and far away from the middle of the bearing and control the freedom degree of angular motion, are constructed into the rolling motion or the transmission motion of the contact morphology of the rolling bodies and/or the transmission elements; the outer ring on one side of the bearing, which has different outer diameters of the first outer ring and the second outer ring, is connected and matched with the bearing box, and the outer ring on the other side is automatically and axially tensioned through an elastic element matched with a screw; the running clearance of the ball rows in the transmission device in the axial direction is matched and pre-tightened by a plurality of elastic elements matched on the plurality of screws, and the running circumferential clearance of the transmission elements in the transmission device in the radial direction is automatically adjusted by matching a plurality of elastic elements matched on the retainer with a plurality of elastic elements on the screws; the combined bearing and/or the transmission device is always in stable gapless precise motion and is used for general machinery.
In particular to the utilization of the technical field of gyroscopic precession effects of precession (precession, cycloidal, nutation) movements of combined bearings and/or transmissions; in a second aspect, the invention provides a precession effect combination bearing and/or stable transmission of a transmission, which is a stable transmission matched with at least one or at least one slope type annular transmission element by symmetrical pairing, wherein one inner ring or outer ring in the stable transmission on the axial side moves in a rotating way, and the other inner ring or outer ring moves in a precession way; has the characteristics that: the ramp angle of the ramp annular transmission element is sized to achieve a transmission ratio of said inner and outer races, said transmission being configured such that a change in at least one parameter of motion is achieved between drive and output, the transmission element of the ramp annular transmission element being formed with at least one of a combination of tapered and cylindrical rollers, asymmetric spherical rollers, balls, gears.
In a third aspect, the invention also relates to the field of passive transmissions with a passive precession (nutation) motion effect, which are characterized in that the axial side transmission rolling surfaces of the passive transmission are correspondingly matched with the transmission elements to support the rotary motion or have a precession motion mode under external moment, and the annular axial transmission rolling surfaces on two sides of the ball center of the inner ring and the outer ring of the axial side transmission rolling surfaces of the passive transmission are matched with the conical transmission rolling surfaces on two sides of the ball center.
In a fourth aspect, the invention also relates to the field of active transmissions with an active precession (nutation) effect, characterised in that the axial side transmission rolling surfaces of the active transmission are adapted to the precession or nutation compound nutation of the corresponding transmission element, and that the oblique cone transmission rolling surfaces on both sides of the centre of sphere of the inner and outer rings of the axial side transmission rolling surfaces of the device are adapted to the annular axial transmission rolling surfaces on both sides of the centre of sphere.
In a fifth aspect, the invention further relates to the field of axial retainers and/or axial planetary carriers of a stable, passive and active transmission device, which is characterized in that the axial retainers and/or the axial planetary carriers are correspondingly oppositely matched in the axial sides, a pair of axial retainers and/or the axial planetary carriers are constructed into annular inner peripheral sides and outer peripheral sides, one axial side of each inner peripheral side is matched in a shaft hole of an outer ring, the outer diameter of the inner peripheral side is smaller than the inner diameter of the shaft hole of the outer ring, and the other axial side is directed to the axial end part of the inner ring and is spaced by a distance; the outer diameters of two sides of each inner circumference side are provided with rubber sealing rings, and the two axial ends of each rubber sealing ring are abutted against the axial end parts of the inner ring and the outer ring; the outer periphery side is matched in the axial space of the inner ring and the outer ring, the pockets are uniformly distributed in the circumference of the inner ring and the outer ring, grooves are formed on two opposite sides of the pockets in the axial direction, the grooves are arranged at two ends of a radial line in a different direction or in the same direction, convex parts formed at two ends of the shaft are matched in the grooves in the pockets in a lap joint manner, the shaft penetrates into a shaft hole of the transmission element, and an elastic element is sleeved at one end of the shaft to control the displacement of the transmission element; according to the structure formed by the transmission element and centrifugal mechanics, the transmission element is provided with two end different diameter parts, the elastic element is matched at the large diameter end of the transmission element to control the circumferential displacement of the transmission element, or the transmission element is provided with two end same diameter parts, the transmission element generates centrifugal force when running at high speed, and the elastic element is matched at one side of the centrifugal force.
In a sixth aspect, the invention also relates to the field of the conversion and utilization of a driving-side rotary motion of a stationary or passive transmission for the driving of a bicycle, with a precessional motion effect.
In a seventh aspect, the invention also relates to the field of devices for a stable or passive transmission device for an internal combustion engine, which are provided with a device for the linear reciprocating motion of a piston to drive the outer ring of the transmission device to precession and drive the inner ring to rotate.
In an eighth aspect, the invention also relates to the field of transmissions utilizing the progressive oblique cross-meshing movement of the teeth of the pin wheel and the cycloid wheel of the precession effect of the cycloid speed reducer or cycloid speed increaser of a stationary transmission.
In a ninth aspect, the invention also relates to the supercharging work of the intake and exhaust of fluid by the linear reciprocating motion of the piston by the precession effect of the fluid machine of the steady-state transmission.
In a tenth aspect, the invention also relates to opposite planetary speed reducing and increasing transmission and/or central split sun wheel opposite speed reducing and increasing transmission by utilizing a combined bearing and/or transmission element of a speed reducer or speed increaser of a transmission device.
Background
Most of the current combined bearings are used as supporting rotary motion, can guide the rotation of a shaft and can also bear a mechanical part of force transmitted by the shaft, and the combined bearings are the relative rotary motion of an inner ring and an outer ring and single sliding motion or rolling motion;
the technical problem that this application actually solved is that rolling motion and sliding motion combined point, line, surface contact's combination bearing of degree of freedom motion, on the other hand combination bearing also can be used as transmission, and they both are mutually connected and act. A detailed description of the interaction of the combination bearing with the transmission will be given below.
In a first aspect, the invention provides a combined bearing and/or transmission device, which is characterized in that spherical raceways of at least one or at least one of inner ring or outer ring are superposed and separated, correspond to raceways in the axial directions of the inner ring and the outer ring, and are matched with different rolling bodies and/or control motion modes of transmission elements; at least one inner ring forms an annular radial spherical raceway and at least two opposite inner balls are formed by the first raceway, the second raceway and/or balls of the inner ring in the axial direction; the bearing comprises a bearing body, at least one outer ring, a plurality of cages, at least one rolling element, at least one transmission element, at least one rolling element and/or at least one transmission element, wherein the at least one outer ring forms a split type variation design of the contact morphology of the inner raceways of the first outer ring and the second outer ring, the spherical raceway spaces of the inner ring and the outer ring, which are radially separated, of the bearing are in point contact rolling motion of a plurality of angular contact ball rows maintained by the axially distributed cages, the rolling element and/or the raceway between the spherical raceways of the inner ring and the outer ring, which are overlapped on the two sides of the middle part of the bearing, the rolling element and/or the raceway between the raceways of the transmission element, which are far away from the middle part of the bearing and control angular motion freedom, are constructed into rolling motion or transmission motion of the contact morphology of the rolling element and/or the transmission element; the outer ring on one side of the bearing, which has different outer diameters of the first outer ring and the second outer ring, is connected and matched with the bearing box, and the outer ring on the other side is automatically axially pre-tightened through an elastic element matched with a screw; the running clearance of the ball rows in the transmission device in the axial direction is matched and pre-stressed by a plurality of elastic elements matched on the plurality of screws, and the running clearance of the transmission elements in the transmission device in the radial direction is automatically and flexibly adjusted by a plurality of elastic elements matched on the retainer and a plurality of elastic elements matched on the screws; the combined bearing and/or transmission device is always in stable gapless accurate motion and is used for general machinery.
The use of combined bearings and/or transmissions as a technical field of gyroscopic precessional effects of interrelated precessional (precessional, cycloidal, nutating) motions.
In a second aspect, the invention provides a stable transmission device of a combined bearing and/or transmission device with precession effect, which controls the rotation motion of an inner ring or an outer ring of the stable transmission device and the precession motion of the inner ring or the outer ring of the other side by symmetrically matching at least one or at least one slope type annular transmission element (slope type circumferential rolling element) matched with a transmission rolling surface on the axial side; has the following characteristics: the ramp angle of the ramped annular drive element being sized to achieve a transmission ratio of the inner race to the outer race, the transmission being configured such that a change in at least one parameter of motion is achieved between drive and output, the drive element of the ramped annular drive element being formed with: at least one of a combination of a tapered roller and a cylindrical roller, an asymmetric spherical roller, a ball and a gear. The tapered rollers are combined into an annular slope, the contact surfaces on the two axial sides of each tapered roller combination form an angle to form a pair of transmission rolling surfaces which are matched with the axial sides of the bearing and/or the device, or two cylindrical rollers are added into each row to form the transmission element of the combination of the tapered rollers and the cylindrical rollers (the national application number is 202280002318.6). The asymmetric spherical rollers are combined into an axial annular slope shape, contact surfaces on two axial sides of each roller combination form an angle to form a pair of transmission rolling surfaces matched with the spherical surfaces on the axial sides of the bearing and/or the device, and the radius of the spherical surfaces on two ends of the roller of the asymmetric spherical roller can be smaller than that of the transmission rolling surfaces in design, which is at least one design mode. In another alternative, the combination of the balls forms a precession motion which is matched and stably controlled in the axial side transmission rolling surface of the bearing and/or the device, and the combination of each ball with different size and diameter forms an annular slope shape, the transmission rolling surface in the axial side is configured into the shapes of a conical transmission rolling surface, a spherical transmission rolling surface, an inclined conical transmission rolling surface, an annular spherical transmission rolling surface and an inclined annular spherical transmission rolling surface (the national application number: 202111007956.0 also has related introduction), wherein the inclination of the central axis of the transmission rolling surface relative to the axis of the transmission shaft is designed into a composite motion of various motions relative to the precession motion. In a further embodiment, the combination of the gears forms a pair of motion-controlled stable precession motions in the bearing and/or the transmission rolling surface on the axial side of the device, the gears are designed in such a way that the pinion set is maintained by the cage and/or the planet carrier, the transmission rolling surface is designed in such a way that the tooth profile of the pinion set is configured, and the transmission motion of the gears is larger than the moment of the friction transmission motion of the rolling bodies in the transmission.
In a third aspect, the present invention provides a passive transmission device with a passive precession (nutation) motion effect, which is characterized in that a transmission rolling surface at the axial side of the passive transmission device and a transmission element are correspondingly matched to support a rotary motion, or have a precession motion mode under an external moment; if the outer ring is driven to make precession movement and the inner ring makes rotation movement, the outer ring is stopped to be driven, the rotation speed of the inner ring is reduced and returns to the supporting rotation movement, and the movement can be continuously repeated;
the transmission elements which are axially opposite are arranged on annular axial transmission rolling surfaces on two sides of a sphere center of an inner ring and an outer ring of an axial side transmission rolling surface and are matched with conical transmission rolling surfaces on two sides of the sphere center;
in the axial direction, the ring plane transmission rolling surfaces of the inner ring and the outer ring at two sides of the spherical center are matched with the conical surface transmission rolling surfaces of the inner ring and the outer ring at two sides of the spherical center, and the transmission elements are conical rollers;
or the annular spherical surface transmission rolling surfaces of the inner ring and the outer ring on two sides of the sphere center are matched with the annular conical spherical surface transmission rolling surfaces of the inner ring and the outer ring on two sides of the sphere center, and the transmission element is an asymmetric spherical roller;
or the transmission rolling surface matched with the conical surface of the outer ring and the axial plane of the inner ring in one side is a ball relative to the transmission element matched with the conical surface of the inner ring in the other side and the axial plane of the outer ring, and the transmission rolling surface is constructed into a planar transmission rolling surface or an annular spherical transmission rolling surface; the axial pair of balls are in point contact motion in the transmission rolling surface;
the speed of the ball responding to the precession motion when the external moment occurs in the supporting back motion of the combined bearing and/or the transmission device is higher than that of the roller. In a fourth aspect, the invention provides an active transmission device with an active precession (nutation) motion effect, which is characterized in that an axial side transmission rolling surface of the active transmission device is matched with a precession motion or a nutation motion composite nutation motion corresponding to a transmission element, and inclined cone transmission rolling surfaces on two sides of a sphere center of an inner ring and an outer ring of the axial side transmission rolling surface of the device are matched with annular axial transmission rolling surfaces on two sides of the sphere center; the design idea is that the transmission element is constructed into a tapered roller, an asymmetric spherical roller and a ball, and the transmission rolling surface at the axial side is constructed into a rolling surface track of the transmission element; another design consideration is that the central axis of the oblique conical drive rolling surface in the axial side is inclined with respect to the axis of rotation of the drive shaft by an angle in the range from more than 0 ° to 5 °, and the taper of the cone is in the range from more than 0 ° to 175 °; the central axes of the inner rings on two sides of the spherical centers of the axial sides of the inner ring and the outer ring and the annular axial transmission rolling surface of the outer ring are coincided with the rotation axis of the transmission shaft, and the central axes of the inner rings on two sides of the spherical centers of the axial sides of the inner ring and the outer ring and the inclined conical transmission rolling surface of the outer ring are intersected with the rotation axis of the transmission shaft; the inner ring or the outer ring of one part rotates, the inner ring or the outer ring of the other part moves in a composite mode, and the central axes of the inclined conical transmission rolling surfaces on the two sides of the spherical center are parallel and intersected in the movement; further, the drive rolling surfaces of each row of balls engaged in the axial side are formed as an annular plane with respect to an oblique conical surface, an annular spherical surface with respect to an annular oblique conical spherical surface, and an axial spherical surface with respect to an oblique spherical surface (the central axis of the spherical surface is inclined with respect to the rotational axis of the drive shaft).
In a fifth aspect, the invention provides an axial retainer and/or an axial planet carrier of a stable, passive and active transmission device, which is characterized in that the axial retainer and/or the axial planet carrier are correspondingly oppositely matched in an axial side, a pair of axial retainers and/or the axial planet carrier are constructed into an annular inner peripheral side and an annular outer peripheral side, one axial side of each inner peripheral side is matched in a shaft hole of an outer ring, the outer diameter of the inner peripheral side is smaller than the inner diameter of the shaft hole of the outer ring, and the other axial side is directed to the axial end part of an inner ring and is separated by a distance; the outer diameters of two sides of each inner circumference side are provided with rubber sealing rings, and the two axial ends of each rubber sealing ring are abutted against the axial end parts of the inner ring and the outer ring; the outer periphery side is matched in the axial space of the inner ring and the outer ring, the pockets are uniformly distributed in the circumference of the inner ring and the outer ring, grooves are formed on two opposite sides of the pockets in the axial direction, the grooves are arranged at two ends of a radial line in a different direction or in the same direction, convex parts formed at two ends of the shaft are matched in the grooves in the pockets in a lap joint manner, the shaft penetrates into a shaft hole of the transmission element, and an elastic element is sleeved at one end of the shaft to control the displacement of the transmission element; according to the structure formed by the transmission element and centrifugal mechanics, the transmission element is provided with two end different diameter parts, the elastic element is matched with the large diameter end of the transmission element to control the circumferential displacement of the transmission element, or the transmission element is provided with two end same diameter parts, the transmission element generates centrifugal force when running at high speed, and the elastic element is matched with one side of the centrifugal force; the transmission elements shown are tapered rollers, asymmetric spherical rollers, balls, and the pockets are configured as the profile of the transmission elements.
In a sixth aspect, the present invention provides a stable or passive transmission device for driving a bicycle, wherein the stable or passive transmission device having a precession effect drives the other one to perform a rotational motion, a gear on a rotating shaft of an inner ring of the transmission device of the bicycle is connected to a gear on a wheel, and a user steps on an outer ring connected to a thrust bearing to perform a swinging or swinging motion to drive the inner ring to perform a rotational motion to drive the wheel to run.
In a seventh aspect, the present invention provides a stable or passive transmission device for an internal combustion engine, comprising means for propelling the outer race of the transmission device by a sequential cyclical movement of a plurality of cylinders of pistons linearly reciprocating around a circular arrangement to thereby drive the inner race in a rotational movement.
In an eighth aspect, the invention is a transmission utilizing progressive oblique cross-meshing movement of the teeth of the pin wheel and the cycloid wheel of the precession effect of the cycloid speed reducer or cycloid speed increaser of a stationary transmission.
In the ninth aspect, the invention utilizes the fluid mechanical precession motion of the stable transmission device to drive the pistons in the circularly distributed cylinders to do linear reciprocating motion, and the fluid suction and discharge pressurization work is inner ring rotation motion, outer ring precession motion and outer ring driven piston motion.
In a tenth aspect, the present invention provides a planetary reduction-and-increase gear unit using a combination bearing and/or a reduction gear unit or a planetary reduction-and-increase gear unit in which the transmission elements of the reduction gear unit or the increase gear unit are opposed, wherein the planetary reduction gear unit is tightly coupled to a housing by an axial inner gear ring (outer ring) having, on one axial side thereof, a first planetary element set (axial transmission element) formed by a plurality of elements equally combined on a tray from an external power, and a second planetary element set (axial transmission element) formed by a plurality of elements equally combined on a tray from a power output side on the other axial side, a central sun gear (inner ring) is interposed between the power output side and the power input side, and the tray of the opposed planetary transmission elements floats while being supported by the power input shaft and the power output shaft, the inner gear ring, and the sun gear; when the power at the input side drives the first planetary transmission element of the input shaft connected with the tray, the sun gear can be driven to rotate, so that the second planetary transmission element at the output side is driven to rotate to drive the output shaft connected with the tray to output power, and the opposite planetary transmission elements revolve along the central axis under the axial diameter ratio of each group of elements (the axial distance of one element relative to the axial distance of the other element or the tooth difference of a small gear set) and along the track of the inner gear sleeve. And/or the central split type sun wheel is in contraposition type speed reducing and increasing transmission, and a group of central step transmission elements are arranged between the first sun wheel and the second sun wheel.
Disclosure of Invention
The invention is based on the object of specifying a combination bearing for a universal machine, and the principle of the stable precession behavior of the combination bearing and/or of a transmission for the transmission of the universal machine, and the principle of the passive precession behavior of the combination bearing and/or of the transmission for the transmission or supporting a rotary motion in the universal machine under external torque, and the combined motion of the active precession and nutation of the combination bearing and/or of the transmission for the universal machine, and an axial cage, a planetary gear with a stable or passive combination bearing and/or of the transmission for the universal machine, and a stable or passive transmission for the bicycle travel, and a stable or passive transmission for an internal combustion engine, and a cycloidal reducer or cycloidal speed increaser with a stable transmission, and a fluid machine with a stable transmission, and a speed reducer or increaser with a combination bearing and/or of a transmission.
The disclosed example apparatus includes improvements to conventional bearings that are novel and non-obvious (or inventive). The examples provided herein are primarily based on the arrangement of the raceways in the axial direction of the bearing to be configured to correspond to the raceway contact surfaces of different rolling elements or transmission elements, or to be configured to correspond to the gear orbital transmission surfaces of different pinion gear sets based on the arrangement of the gears in the axial side of the transmission, and to form a movement of the integral bearing in point contact of the ball rows in the radial direction, line contact of the rolling elements or transmission elements in the axial direction and surface contact of the inner and outer races, while the resilient element has a pretension in the radial direction and in the axial direction, the rolling elements or transmission elements in the axial side and the raceways in the axial side being provided with inventive angular degrees of freedom to control the precessional (nutating, precessional) movement of the bearing or transmission, so as to distinguish the present invention from any known prior art at present time.
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. And the combination bearing may also be referred to as a transmission. And the first outer ring and the second outer ring can be mutually switched (the left-right switching relation is convenient for description). The invention adopts the technical scheme that the invention achieves the aim that:
a combination bearing, which can also form a transmission in different arrangements, so to speak combines the pure rolling bearing function itself and the transmission movement due to the high precession (nutation) movement effect in one structural unit. The combined bearing and/or the transmission device forms rolling friction transmission on one aspect, for example, the transmission device is provided with a rolling body transmission on the axial side, and the transmission device can be used as transmission motion with precession motion effect and can also be used as composite motion for supporting rotary motion and precession motion; on the other hand, gear transmission is formed, for example, gear set transmission is arranged on the axial side, and transmission motion and supporting rotation motion can be formed; the combined bearing and/or transmission device comprises an outer ring (an inner gear ring sleeve) and an inner ring (a sun gear), a plurality of rows of rolling bodies and/or transmission elements, a planetary element set, a retainer and/or a planetary tray, a connecting screw and an elastic element, wherein the outer ring or the inner ring of at least one side in the radial direction is constructed into a spherical raceway surface with concave-convex steps, and an inner spherical raceway formed by a concave part of the outer ring is a spherical raceway with coincident ball centers relative to an outer spherical raceway formed by a convex part of the inner ring;
in an advantageous design, the stable transmission device is matched with at least one slope type annular transmission element, the slope type annular transmission element is correspondingly matched on two sides of the inner ring and the outer ring in the axial direction, a plurality of transmission elements of the slope type annular transmission element are uniformly distributed by the annular axial retainer, and each transmission element of the slope type annular transmission element forms an angle in a slope type around the annular shape, namely, the side surface of a plurality of transmission element combinations of the circular array penetrates through a central axis and is folded into a diagonal line and is split into a pair;
the inner ring and the outer ring in the radial direction form spherical raceways which are overlapped relative to the centers of matched steps, namely, the spherical raceways of the inner ring and the outer ring are separated and overlapped to form at least two spherical raceways of at least one step;
the outer ring forms a split outer ring matched with at least one of the two in the axial direction, and the outer diameters of the two outer rings are different or the same;
the ball rows are in contact with the spherical raceway in a point manner, so that the ball rows are easy to roll and firstly bear at least one part of load, and the superposed spherical raceway surfaces of the inner ring and the outer ring are easy to be in sliding contact and bear the other part of load;
the two outer sides of the split outer ring in the axial direction are partially coated with a distance to form a transmission rolling surface in the matched axial side of the inner ring and the outer ring and a corresponding of a spherical roller path formed by overlapping and separating the inner ring and the outer ring, so that the slope type annular transmission element is constructed into a transmission element of the transmission rolling surface;
a plurality of bolt holes matched with at least one split outer ring are formed in the outer periphery of the outer side of the split outer ring in the axial direction, the two outer rings are oppositely connected through the bolts matched with at least one split outer ring, and the outer ring on one side of the split outer ring is in interference fit with the bearing box body;
the running clearance of the ball rows in the transmission device in the axial direction is matched and pre-stressed by a plurality of elastic elements matched with the bolts, and the running circumferential clearance of the slope type annular transmission element in the transmission device in the radial direction is automatically flexibly adjusted by a plurality of elastic elements matched with the elastic elements on the bolts on a retainer;
the slope type annular transmission element is constructed to control the precession motion of the inner ring and the outer ring in the transmission rolling surface motion correspondingly in the combined rolling ratio and flexibility of the rolling motion of at least one pair of ball rows of the inner ring and the outer ring and the sliding motion of the coincident spherical raceways of the inner ring and the outer ring;
the transmission device with the slope type annular transmission element drives the inner ring to rotate so as to drive the outer ring to perform precession motion towards the other direction, and/or the transmission device with the slope type annular transmission element drives the outer ring to rotate so as to drive the inner ring to perform precession motion towards the other direction, and/or the outer ring or the inner ring of one party performs precession motion so as to drive the inner ring or the outer ring of the other party to perform rotational motion towards the opposite direction;
the ramp angle of the ramped annular drive element is sized to achieve a drive ratio of the inner race to the outer race, the transmission being configured such that a change in at least one parameter of motion is achieved between drive and output;
the transmission elements of the slope type annular transmission element can be designed into transmission elements and balls, wherein the transmission elements are conical rollers, asymmetric spherical rollers, and the transmission rolling surfaces of the transmission elements on the axial side move in a contact friction mode; in a further embodiment, the transmission element is formed as a pinion gear train and an intersecting shaft transmission, the transmission running surfaces of which are configured as the tooth profiles of the gears: the transmission surface of the transmission element pinion set on the axial side moves into tooth-tooth contact friction motion; the device is constructed in opposed pairs with at least one inner ring (sun gear) of an inner center, at least one pair of transmission elements fitted on both sides of the inner center, and at least one pair of outer rings (inner toothed rings) surrounding both of them and having a through hole of a common rotation center line.
In the advantageous embodiment described above, the outer ring can also be arranged in such a way that,
the outer ring also comprises a first split outer ring and a second split outer ring, the first outer ring and the second outer ring are arranged in a cover ring shape, wherein the outer diameter of the outer ring on one side of the first combined outer ring and the outer ring on the other side of the first combined outer ring is slightly smaller than that of the outer ring on the other side of the first combined outer ring and/or the outer diameters of the outer rings on two sides of the first combined outer ring and the second combined outer ring are the same; and the outer ring with the large outer diameter on one side of the combined outer ring is in interference fit with the bearing box, and/or the outer rings with the same outer diameters on the two sides of the combined outer ring are in interference fit with the bearing box.
The section of the combination of the first outer ring and the second outer ring in the cover ring shape is approximately in a concave shape, each part of the outer ring in the cover ring shape forms a three-stage step, the first stage step of the three-stage step is the middle part of the combination of the first outer ring and the second outer ring in the axial direction of the bearing, the second and third stage steps of the three-stage step extend towards the rotation axis direction of the bearing, each step of the outer ring forms two annular end faces in the axial direction and the radial direction, the end face in the axial direction of the first step of the combination of the first outer ring and the second outer ring is the abutting part of the two outer rings and a first inner cavity spherical raceway with spherical inside in the radial direction, the end face in the axial direction of the second step is a cavity (a first spherical inner cavity spherical raceway) which is connected with the end face in the radial direction of the first step and forms the combination of the first step, the end face in the radial direction of the second step forms a spherical second inner spherical raceway and has the same diameter as the outer spherical raceway of the inner ring, the inner end face in the axial direction of the third step is a radial direction which is connected with the end face in the radial direction of the second step and forms a radial direction of the inner ring raceway corresponding to the inner ring raceway, and the third inner ring raceway, and the rolling surface of the third step can pass through the axial direction of the rolling shaft; the outer end face of the third step in the axial direction is an annular end face connected with the third step in the radial direction and forms an outer annular plane, and the outer portion of the first step in the radial direction is the outer diameters of the first outer ring and the second outer ring and is connected with the outer annular plane of the third step in the axial direction.
The end faces of the adjacent parts of the first outer ring and the second outer ring are positioned on a radial extension line of a bearing spherical center and/or are offset relative to the radial extension line of the bearing spherical center, and the distances from the transmission rolling surfaces of the third ball tracks of the first outer ring and the second outer ring to the bearing spherical center are equal and/or unequal, so that the transmission rolling surfaces of the third ball tracks are configured into a contour contact shape of a transmission element.
In an advantageous embodiment, the ramp angle of the ramp-like annular transmission element ranges from more than 0 ° to 10 °, preferably from more than 0 ° to 6 °.
In an advantageous embodiment, the passive transmission device is paired with at least one of the rolling elements, the rolling elements are oppositely matched on two sides of the inner ring and the outer ring in the axial direction, and the plurality of rolling elements are uniformly distributed by the annular axial retainer;
the inner ring and the outer ring in the radial direction form spherical raceways which are overlapped relative to the centers of the matched steps, namely, the spherical raceways of the inner ring and the outer ring are separated and overlapped to form two spherical raceways of at least one step;
the outer ring forms a split outer ring matched with at least one of the two in the axial direction, and the outer diameters of the two outer rings are different;
the two outer sides of the split outer ring in the axial direction are partially coated with a distance part to form transmission rolling surfaces in the axial direction of the inner ring and the outer ring which are matched with each other, namely, the transmission rolling surface of the inner ring on one axial side of the spherical center is a conical rolling surface of which the conical rolling surface is matched with the transmission rolling surface of the outer ring on the other axial side of the spherical center, and the annular axial transmission rolling surfaces of the inner ring and the outer ring are correspondingly matched with the conical transmission rolling surfaces; such that the rolling bodies are configured as rolling bodies of said transmission rolling surface;
the ball rows are in contact with the spherical raceway in a point manner, so that the ball rows are easy to roll and firstly bear at least one part of load, and the superposed spherical raceway surfaces of the inner ring and the outer ring are easy to be in sliding contact and bear the other part of load;
a plurality of bolt holes matched with at least one of the split outer rings are formed on the outer periphery of the outer side of the split outer ring in the axial direction, the two outer rings are oppositely connected through the plurality of bolts matched with at least one of the split outer rings, and the outer ring on one side of the split outer ring is in interference fit with the bearing box body;
the running clearance of the ball rows in the transmission device in the axial direction is matched and pre-stressed by a plurality of elastic elements matched with the bolts, and the running circumferential clearance of the transmission rolling bodies in the transmission device in the radial direction is automatically flexibly adjusted by a plurality of elastic elements matched with the retainer and the elastic elements on the bolts;
the transmission rolling body is constructed to relatively control at least one motion of precession motion and/or support revolution motion of the inner ring and the outer ring in the transmission rolling surface motion correspondingly in the operation of at least one of the combined sliding-rolling ratio and the flexibility freedom of the rolling motion of at least one pair of ball rows of the inner ring and the outer ring and the sliding motion of the coincident spherical roller paths of the inner ring and the outer ring under at least one external moment;
the conical transmission rolling surfaces on two sides of the spherical centers of the inner ring and the outer ring are matched with the transmission device of the annular axial transmission rolling surface to drive the inner ring to rotate, the outer ring carries out precession motion towards the other direction under the external moment, and/or the conical transmission rolling surfaces on two sides of the spherical centers of the inner ring and the outer ring are matched with the transmission device of the annular axial transmission rolling surface to drive the outer ring to rotate, the inner ring carries out precession motion towards the other direction under the external moment, and/or the outer ring or the inner ring of one party carries out precession motion to drive the inner ring or the outer ring of the other party to carry out rotary motion towards the opposite direction, and/or the outer ring or the inner ring of one party carries out rotary motion to drive the inner ring or the outer ring of the other party to carry out relative supporting rotary motion;
the transmission ratio of the inner ring and the outer ring is realized by the taper arrangement of the conical surface of the transmission rolling surface relative to the precession motion and the matching arrangement of the transmission rolling body, and the transmission device is constructed to realize the change of at least one motion parameter between the driving and the output;
the conical rolling surface of the transmission rolling surface is designed for at least one roller, and rolling bodies of the device can be selected from different cages;
the transmission rolling bodies or transmission elements can be designed into tapered rollers, asymmetric spherical rollers and balls, and the transmission rolling surface motion of the transmission elements on the axial side is contact friction motion; in a further embodiment, the transmission element is formed as a pinion set: the transmission device comprises a conical gear, an asymmetric spherical gear and a transmission rolling surface matched with a small gear set to form orbital transmission surfaces with different tooth profiles, wherein the orbital surface motion of the transmission element small gear set at the axial side is tooth-tooth contact friction motion, the tooth-tooth contact friction motion can only be used as supporting rotation motion and transmission motion in the tooth-tooth matching motion, and point contact rolling, surface contact sliding motion and tooth contact rolling transmission motion of a ball row are formed inside the transmission device.
In an advantageous embodiment, the active transmission device is matched with at least one rolling element for transmission, the rolling elements are oppositely matched on two sides of the inner ring and the outer ring in the axial direction, and the plurality of rolling elements are uniformly distributed by the annular axial retainer;
the inner ring and the outer ring in the radial direction form spherical raceways which are overlapped relative to the centers of matched steps, namely, the spherical raceways of the inner ring and the outer ring are separated and overlapped to form two spherical raceways of at least one step;
the outer ring in the axial direction forms a split outer ring matched with at least one of the two outer rings, and the outer diameters of the two outer rings are different;
the two outer sides of the split outer ring in the axial direction are partially coated with a distance part to form transmission rolling surfaces in the axial direction of the inner ring and the outer ring which are matched with each other, namely, the central axis of the conical transmission rolling surface of the outer ring on one axial side of the spherical center and the central axis of the conical transmission rolling surface of the inner ring on the other axial side of the spherical center are inclined relative to the central axis of the transmission shaft and the central axes of the inclined conical transmission rolling surfaces of the inner ring and the outer ring are crossed and parallel in motion, and the annular axial transmission rolling surfaces of the inner ring and the outer ring are matched with the inclined conical transmission rolling surfaces correspondingly; such that the rolling bodies are configured as rolling bodies of said transmission rolling surface;
the ball rows are in contact with the spherical raceway in a point manner, so that the ball rows are easy to roll and firstly bear at least one part of load, and the superposed spherical raceway surfaces of the inner ring and the outer ring are easy to be in sliding contact and bear the other part of load;
a plurality of bolt holes matched with at least one split outer ring are formed in the outer periphery of the outer side of the split outer ring in the axial direction, the two outer rings are oppositely connected through the bolts matched with at least one split outer ring, and the outer ring on one side of the split outer ring is in interference fit with the bearing box body;
the running clearance of the ball rows in the transmission device in the axial direction is matched and pre-stressed by a plurality of elastic elements matched with the bolts, and the running circumferential clearance of the transmission rolling bodies in the transmission device in the radial direction is automatically flexibly adjusted by a plurality of elastic elements matched with the retainer and the elastic elements on the bolts;
the transmission rolling body is constructed into at least one compound motion of relatively controlling the precession motion and/or nutation motion of the inner ring and the outer ring in the transmission rolling surface motion correspondingly in the operation of at least one of the combination of the rolling ratio and the flexibility freedom of the rolling motion of at least one pair of ball rows of the inner ring and the outer ring and the sliding motion of the coincident spherical roller paths of the inner ring and the outer ring;
the transmission device with the inclined conical transmission rolling surfaces on two sides of the spherical centers of the inner ring and the outer ring is matched with the annular axial transmission rolling surface to drive the inner ring to rotate, the outer ring performs precession motion towards the other direction, and/or the transmission device with the inclined conical transmission rolling surfaces on two sides of the spherical centers of the inner ring and the outer ring is matched with the annular axial transmission rolling surface to drive the outer ring to rotate, the inner ring performs precession motion towards the other direction, and/or the outer ring or the inner ring of one party performs precession motion to drive the inner ring or the outer ring of the other party to perform rotation motion towards the opposite direction;
the angle and taper setting of the central axis of the oblique cone of the drive rolling surface relative to the compound motion effects a drive ratio of the inner and outer races, the drive being configured such that a change in at least one motion parameter is effected between drive and output;
the transmission rolling bodies or transmission elements can be designed into tapered rollers, asymmetric spherical rollers and balls, and the transmission rolling surface motion of the transmission elements on the axial side is contact friction motion; the central axes of the inner rings on two sides of the spherical centers of the axial sides of the inner ring and the outer ring and the annular axial transmission rolling surface of the outer ring are coincided with the rotation axis of the transmission shaft, and the central axes of the inner rings on two sides of the spherical centers of the axial sides of the inner ring and the outer ring and the inclined conical transmission rolling surface of the outer ring are intersected with the rotation axis of the transmission shaft; the inner ring or the outer ring of one part rotates, the inner ring or the outer ring of the other part moves in a composite mode, and the central axes of the inclined conical transmission rolling surfaces on the two sides of the spherical center are parallel and intersected in the movement; further, the drive rolling surfaces of each row of balls engaged in the axial side are formed as an annular plane with respect to an oblique conical surface, an annular spherical surface with respect to an annular oblique conical spherical surface, and an axial spherical surface with respect to an oblique spherical surface (the central axis of the spherical surface is inclined with respect to the rotational axis of the drive shaft).
In an advantageous design, an axial cage and/or a planetary pallet of a stationary or passive or active transmission, according to which the two side transmission rolling surfaces in the axial direction of the split outer ring and the two side transmission rolling surfaces in the axial direction of the inner ring are configured to configure the transmission rolling surfaces of the pair of transmission elements; the pair of transmission elements in the axial direction are configured by the axial cage to engage the ball rows to facilitate movement of the transmission rolling surfaces in contact in the axial direction of the transmission and are guided by the cage to maintain contact between the transmission rolling surfaces in the axial direction;
the section of the annular retainer forms a T-shaped inner circumferential side and an outer circumferential side, the upper part of one T-shaped rotation circle is the inner circumferential side, the lower part of the T-shaped rotation circle is the outer circumferential side, two sides of the annular section of the inner circumferential side form corresponding slope shapes and/or parallel shapes, a certain distance is reserved between the edge of the inner end face of an axial shaft hole extending towards the outer ring on one side of the T-shaped upper part and the edge of the axial side end face extending towards the inner ring on the other side of the T-shaped upper part, rubber sealing rings are sleeved on the annular outer diameters on two axial sides of the T-shaped upper part and abut against the axial parts of the inner ring and the outer ring, and window-type pockets are formed on the outer circumferential side of the T-shaped lower part;
the axial retainer window pocket is in the shape of a transmission element, two sides of the axial line of the window pocket radiating relative to the central rotating shaft of the retainer are provided with axially opposite or axially equidirectional two-side grooves which are matched and connected with a mandrel, the axial lines of the axially opposite or axially equidirectional two-side grooves are in conical radiation or are vertically radiated relative to the central rotating shaft of the retainer, and the mandrel is in a structure that concave-convex parts formed at two ends of a round rod are correspondingly matched in the grooves at two sides of the window pocket; the mandrel penetrates through flange-shaped elements matched with two ends of a shaft hole of the transmission element, the elastic element penetrates through the mandrel and is configured on the large-diameter end side of at least one of the transmission elements, one side of the elastic element is abutted against the radial end line part or the end part of the window-type pocket, and the other side of the elastic element is abutted against the flange-shaped element end face; a two-part snap-in device is arranged in the window pocket region of the retainer, which device forms a two-part snap-in device by means of a terminal or an end and an end face, the two-end flange disk-shaped element on the transmission element being in abutment with the radial terminal or the end of the window pocket and the spring element for retaining the transmission element in the pocket, the two-part snap-in device allowing the insertion of the transmission element into the pocket by means of elastic deformation in one face of the spring element and in the region of a terminal or an end of the window pocket; the axes of rotation of the plurality of transmission elements are arranged around a conical radiation or are arranged perpendicular to the central axis of rotation of the cage; on the one hand, the circumferential displacement of the transmission element is controlled by a radial force of the elastic element on the holder in cooperation with a force of the axial elastic element, and on the other hand, the conical transmission element is kept in contact with the transmission rolling surface in the axial side, the conical transmission element allows for precision deviation during manufacturing and processing, and in the convergence of the axial force and the radial force, the end surface of the flange on one side of the conical transmission element is not in contact with one end line part or one end part of the window-type pocket.
In an advantageous embodiment, the ramp-type ring transmission element is flexibly preloaded by an elastic element on a bolt in the device in cooperation with an elastic element on the retainer.
In an advantageous embodiment, a stable transmission device is provided, which is based on the stable transmission device paired with at least one ramp-type ring transmission element, an axial cage, wherein the transmission elements of the ramp-type ring transmission element are sleeved by a pinion gear set to run in transmission rolling surfaces on the axial sides of the inner and outer rings, and the transmission rolling surfaces are configured as gear teeth of a ring-shaped face gear; the annular plane gear on the axial side of the outer ring is composed of independent flat rings, and a plurality of convex parts are arranged on the opposite surfaces of the annular plane gear on the flat rings and matched with a plurality of concave parts on the axial side of the outer ring to form the two-side annular plane gear of the split outer ring.
In an advantageous design, a stable or passive transmission device is used for driving a bicycle, according to the stable or passive transmission device, the user steps on the outer ring of the transmission device movably connected with the thrust bearing of the pedal by two feet to do a rotational and precessional motion to drive the inner ring to rotate, and a bevel gear fixedly connected with an output shaft connected with the inner ring drives a bevel gear fixedly connected with a wheel to drive the wheel to run;
the power device of the bicycle is further designed to be vertically connected with a pedal, a thrust bearing, a transmission device, an output shaft and a downward bevel gear from top to bottom, and a positioner is arranged on the output shaft between the transmission device and the bevel gear; the structure of the wheel is that the left and right double-row wheels are connected by a middle shaft, two ends of the middle shaft are connected with a surrounding rod and a connecting rod, the inner side of each wheel of the double-row wheels is connected with a first bevel gear and a second bevel gear, a bevel gear is arranged between the first bevel gear and the second bevel gear, and one side of the first bevel gear and one side of the second bevel gear are in left-right moving positioning contact meshing with the bevel gear through a positioner; the positioner comprises an adjusting screw rod, a sleeve and a rolling bearing combination, wherein the rolling bearing is arranged in the oval sleeve and movably connected, the inner ring of the rolling bearing is connected with an output shaft, the outer ring of the rolling bearing is connected with the sleeve, two ends of the sleeve are connected with two sides of a surrounding rod, the left adjusting screw rod and the right adjusting screw rod penetrate through a through hole of the surrounding rod and a sleeve through hole and are matched with each other to extrude the rolling bearing to enable a bevel gear to be meshed with a first bevel gear and a second bevel gear on one side of the bevel gear, the lower part of a front fork is movably connected with a connecting rod, the upper part of the front fork is movably connected with the upper part of the surrounding rod, a front wheel is arranged at the lower end of the front fork, and a steering wheel is arranged at the upper end of the front fork. The user adjusts the wheel driving on the side to advance according to the motion swinging habit of the user.
The stable transmission device is adopted in the design, one foot of a user steps on the pedal, the other foot pushes the driving wheel to rotate, meanwhile, the foot is lifted to do rotating and swinging motion on the pedal, the bicycle runs, when the user stops moving, the inertia of the wheel motion can drive the stable transmission device to do precession motion all the time, and the stable transmission is mutual transmission; in another design, a passive transmission device is adopted, after a user drives a wheel to rotate, the user stops moving, an outer ring of the passive transmission device stops precession, the inner ring and the outer ring form pure rolling under the action of inertia, the device is converted into supporting rotation motion, the user continues to swing precession motion (external force), the outer ring of the passive transmission device precesses, the inner ring is driven to form moment rotation, and the device is converted into driving motion of the wheel.
In an advantageous embodiment, a stationary or passive transmission for an internal combustion engine comprises: a drive shaft assembly including a central drive shaft;
a cylindrical cylinder block having a longitudinal central axis with a central longitudinal opening for receiving the drive shaft, the cylindrical cylinder block further defining: a plurality of combustion chambers each having an axis parallel to the central axis, the combustion chambers defined on a circle concentric with the longitudinal central axis, each of the combustion chambers having a generally cylindrical sidewall, a first closed end and a second open end, and an intake valve opening and an exhaust valve opening defined in the first closed end of each combustion chamber;
a coolant system including a plurality of coolant channels;
a plurality of intake passages, each in fluid communication with one of the intake valve openings;
and
a plurality of exhaust passages, each of which is in fluid communication with one of the plurality of exhaust valve openings;
a plurality of piston assemblies each having a piston received within one of the combustion chambers;
one end of each connecting rod is correspondingly connected with the piston spherical hinges;
a plurality of connecting rod bases, each of which is correspondingly connected with the other end spherical hinge of the plurality of connecting rods;
an annular base plate provided at an opposite end of the engine block and provided with a plurality of bosses, each of which is correspondingly connected with a plurality of link bases; and
a valve train including a plurality of intake valves and a plurality of exhaust valves, each of the valves being received in one of the valve openings within the combustion chamber;
the transmission of the internal combustion engine further includes: comprising a stationary, passive transmission according to the above, said thrust bearing being arranged at the opposite end of the engine block, said annular chassis being arranged on one side of said thrust bearing, said transmission being arranged on the other side of said thrust bearing; the engine central driving shaft is in running fit with a bearing arranged at the central longitudinal opening in the engine cylinder body and the inner ring of the transmission device; the ignition expansion of the circulation in the cylinder drives each piston to do linear reciprocating circular motion, each connecting rod is pushed to do circular motion to drive the annular chassis and the thrust bearing respectively and sequentially, so that the outer ring of the transmission device is further driven to do rotary swinging precession motion, and the central driving shaft connected with the inner ring does rotary motion, so that the output of rotating speed and power is realized;
the stable transmission device is adopted in the design, the device is started by the rotation of a central driving shaft driven by a starter, the circular ignition expansion in the cylinder drives each piston to linearly reciprocate, when the ignition is stopped, the inertia of the movement of the central driving shaft drives the stable transmission device to move all the time, and each piston linearly reciprocates in a circular manner; in another design, a passive transmission device is adopted, the device is started by a starter to drive a central driving shaft to rotate, the ignition expansion circulating in a cylinder drives each piston to do reciprocating circular motion, the central driving shaft does rotary motion, when the ignition is stopped, each piston stops moving, the central driving shaft does inertial rotary motion, the passive transmission device is converted into idle motion for supporting rotary motion, and when the ignition expansion is continued to drive each piston to do reciprocating circular motion and the outer ring swings and revolves, the passive transmission device is converted into rotary motion for driving the inner ring to form moment. The same functional principle as described above.
In an advantageous embodiment, a cycloidal reducer or cycloidal speed increaser of a stationary transmission is used, which cycloidal reducer or speed increaser comprises, in accordance with the stationary transmission, an axial cage: the device comprises a first rolling bearing, a second rolling bearing, a cover wheel, a precession needle gear, a transmission device, a steel ball body, an input shaft and a shell;
the procession needle gear is arranged into a conical body, a needle groove is formed in the periphery of the conical body, the needle teeth are movably matched in the needle groove, the procession needle gear is sleeved on an outer ring on one side of the transmission device and fixedly connected, and a pin is inserted into a matching groove of the procession needle gear and the transmission device;
the inner periphery of the cover wheel is provided with inner teeth, the axial center of the cover top is provided with an output shaft, the inner bottom of the axial center of the cover wheel is provided with a spherical concave part, and the outer periphery of the cover wheel is connected with the inner ring of the first rolling bearing in a matched manner;
the outer ring of the first rolling bearing is connected with the shell in a matching way;
the conical needle teeth of the precession needle gear are matched in the inner teeth of the cover gear;
the outer axial center of the outer ring at one side of the transmission device is provided with a spherical concave part, and the ball is matched in the spherical concave parts of the cover wheel and the outer ring of the transmission device;
one side of the input shaft is connected with the inner ring of the transmission device in a matching way, and the other side of the input shaft is fixedly connected with the inner ring of the second rolling bearing;
the outer ring of the second rolling bearing is fixedly connected with the shell;
the shell is a half gourd ladle-shaped shell, a large-diameter inner chamber of the shell is connected with the first rolling bearing in a matching way, and a small-diameter inner chamber of the shell is connected with the second rolling bearing in a matching way, namely, the first rolling bearing, the second rolling bearing, the cover wheel, the precession pin gear, the transmission device and the shaft are wrapped in two half gourd ladle shapes, and the shell is radially connected by bolts; an elastic element is arranged between the outer edge of the large-diameter inner chamber of the shell and the axial side end of the outer ring of the first rolling bearing; the elastic element is embedded into one of the grooves; the outer edge of the small-diameter inner chamber of the shell wraps the axial side end of the outer ring of the second rolling bearing; the first rolling bearing and the second rolling bearing are formed into a back-to-back mode of a bearing of a tapered roller;
the input shaft drives the inner ring of the transmission device to rotate, the precession needle gear on the outer ring of the transmission device is driven to perform revolution (precession) and autorotation motion, the needle teeth of the precession needle gear are in oblique line cross meshing with the inner teeth on the cover gear, the teeth in oblique line cross meshing with the inner teeth are in progressive contact, the precession and revolution of the precession needle gear are performed simultaneously, and the autorotation motion drives the output shaft of the cover gear to perform deceleration motion;
the ratio of the internal teeth to the needle teeth can form at least two teeth of at least one party, the tooth difference is 1-9 to 20 times of teeth, the multiples of the internal teeth and the teeth of the needle teeth can be interchanged, and the needle teeth are meshed with the first teeth of the internal teeth when the inner ring rotates for one circle, and compared with the slope with a large angle, the teeth of the needle teeth are fewer in precession (rotation). When the cover wheel is used as a cycloid speed increaser, the output shaft is converted into an input shaft to rotate at a low speed, the internal teeth of the cover wheel rotating at the low speed drive the needle teeth of the precession needle gear to do precession motion, and the output shaft connected with the inner ring rotates at an increased speed to output. In another embodiment, the precession pin gear is provided with a cylindrical shape corresponding to the cover wheel, or the precession pin gear is provided with a cone-shaped body corresponding to the inner periphery of the cover wheel and provided with an outward conical inner tooth.
In an advantageous embodiment, a cycloidal reducer or cycloidal speed increaser of a stationary transmission is used, which, depending on the stationary transmission and the axial cage, comprises: the device comprises a precession cycloid wheel, a pinwheel, a first rolling bearing, a second rolling bearing, a driven wheel, an input shaft and a shell;
the precession cycloidal gear is arranged in a conical cover shape, the cover bottom of the precession cycloidal gear is provided with a plurality of through round parts, the periphery of the precession cycloidal gear is provided with conical external teeth, the inner periphery of the precession cycloidal gear is sleeved on the outer ring at one side of the transmission device and fixedly connected with the outer ring, and a pin is inserted into the matching grooves of the precession cycloidal gear and the transmission device;
a needle groove is formed in one side of the inner periphery of the needle wheel, the needle teeth are movably matched in the needle groove, an annular flange is arranged on the other side of the inner periphery of the needle wheel, and the outer periphery of the annular flange is fixedly connected with the shell;
the inner periphery of the annular flange of the pin wheel is fixedly connected with the outer ring of the first rolling bearing;
an output shaft is arranged on one side of the driven wheel, a plurality of circular convex parts are arranged on the other side of the driven wheel, and the periphery of the circular convex parts is connected with an inner ring of the first rolling bearing in a matched mode;
the circular convex parts of the driven wheel are matched in the through circular parts of the precession cycloidal gear, and the diameter of the through circular part of the precession cycloidal gear is larger than that of the circular convex parts of the driven wheel; the contact surface of the further circular convex part and the through circular part is configured into a precession rotation inclination angle of the transmission device;
one side of the input shaft is connected with an inner ring of the transmission device in a matching way, the other side of the input shaft is connected with an inner ring of a second rolling bearing in a matching way, and an outer ring of the second rolling bearing is fixedly connected with the shell;
the shell is a half gourd ladle-shaped shell, a large-diameter inner chamber of the shell is connected with the outer diameter of the pinwheel in a matched mode, and a small-diameter inner chamber of the shell is connected with the second rolling bearing in a matched mode, namely, the pinwheel and the second rolling bearing are wrapped by the two half gourd ladle-shaped shells and are radially connected with the shell through bolts;
the input shaft drives an inner ring of the transmission device to rotate, the precession cycloidal gear on an outer ring of the transmission device is driven to perform precession (revolution), the conical outer teeth of the precession cycloidal gear are in oblique cross meshing with the movably connected needle teeth on the fixed needle gear, the teeth in oblique cross meshing with the fixed needle gear are in progressive contact, the precession of the precession cycloidal gear forms low-speed rotation of external tooth revolving moment meshed with the needle teeth so as to drive the driven wheel to rotate, and the driven wheel forms at least one order of magnitude of rotation deceleration motion under the difference of the tooth number of the two and the low-speed rotation.
The tooth difference is 1-20 teeth, and the tooth difference can be converted. When the output shaft and the input shaft are interchanged, a cycloid speed increaser is formed. Under the characteristics, in another design, the precession cycloidal gear is provided with a cylinder corresponding to the needle wheel, or the precession cycloidal gear is provided with a conical cover corresponding to one side of the inner circumference of the needle wheel and provided with an outward conical needle groove, the needle teeth are movably matched in the needle groove, and the other side of the inner circumference is provided with an annular flange. In an advantageous embodiment, a fluid machine with a stationary transmission comprises: a central rotating shaft is arranged at the center of the rotary shaft,
a dome cover having a central opening and a plurality of circular holes evenly distributed around the central opening;
a round cup cylinder having a longitudinal central axis with a central longitudinal bottom opening for receiving said rotating shaft and a plurality of fluid openings in the cup wall, said dome fitting over the rim of the cylinder, the round cup cylinder further defining:
a plurality of chambers each having a central axis parallel thereto are disposed within the cylinder, each of the chambers having a generally cylindrical sidewall, a first closed end and a second open end, and a fluid inlet door opening and a fluid outlet door opening defined in the first closed end of each chamber, the plurality of chambers being defined on a circle concentric with the central axis, and the second open ends each communicating with the plurality of circular apertures of the dome cover;
a plurality of suction passages each in fluid communication with one of the access door openings;
and
a plurality of discharge passages, each of which is in fluid communication with one of the plurality of discharge door openings and the plurality of fluid openings;
a plurality of piston assemblies each having a piston received within one of the chambers;
one end of each connecting rod is correspondingly connected with the piston spherical hinges;
a plurality of connecting rod bases, each of which is correspondingly connected with the other end spherical hinge of the plurality of connecting rods;
an annular base plate provided at an opposite end of the dome cover of the cylinder body, and provided with a plurality of bosses, each of which is correspondingly coupled with a plurality of link bases; and
an intake and exhaust door mechanism including a plurality of intake doors and a plurality of exhaust doors, each of the intake doors being received in one of the intake and exhaust door openings within or outside the chamber;
the transmission device of the fluid machine further includes: the stable transmission device and the axial retainer are arranged on the bearing seat; the thrust bearing is arranged at the opposite end of the cylinder body of the fluid machine, the annular chassis is arranged on one side of the thrust bearing, and the transmission device is arranged on the other side of the thrust bearing;
the central rotating shaft of the fluid machine is in rotating fit with a bearing penetrating through the central longitudinal bottom opening of the cylinder body of the fluid machine, a bearing arranged at the central opening of the dome cover and the inner ring of the transmission device;
the central rotating shaft of the fluid machine is driven to drive the inner ring of the transmission device to rotate, the outer ring is driven to do rotational and swinging precession motion, the thrust bearing and the annular chassis are pushed to drive each connecting rod to respectively and sequentially perform cyclic motion, each piston is driven to linearly reciprocate to perform cyclic motion, and the fluid is sucked → discharged from the door inlet and outlet mechanism.
In an advantageous embodiment, the planetary reduction/acceleration gear is supported in a floating manner by means of a split inner ring (the axial side of the split outer ring can form a ring gear or an axial raceway surface) on one axial side, which is tightly connected to the housing, a first planetary element set (axial transmission element) which is driven by external power and is split into several elements on a carrier, and a second planetary element set (axial transmission element) which is split into several elements on the other axial side, which is split into several elements on a carrier, are arranged on one axial side of the inner ring, and a central sun driven wheel (the axial side of the inner ring can form a ring gear or an axial raceway surface) between the output side and the input side, the carrier of the opposing planetary transmission element being supported in a floating manner on the input shaft and the output shaft, the inner ring and the sun driven wheel; when the power on the input side drives the first planetary transmission element of the input shaft connected with the tray, the sun driven wheel is driven to rotate, so that the second planetary transmission element on the output side is driven to rotate to drive the output shaft connected with the tray to output power, and the opposite planetary transmission elements revolve along the central rotation axis under the axial diameter ratio of each group of elements (the axial distance of one element relative to the axial distance of the other element or the tooth difference of a small gear set) and along the track of the inner gear sleeve. The planetary transmission element group is arranged as follows: rolling elements, pinion sets, ramp-type annular rolling elements (transmission elements), ramp-type annular gear sets (transmission elements). The rolling bodies in the axial side are in rolling friction transmission, the pinion gear set in the axial side is in gear friction transmission, and the central sun driven wheel performs balanced rotary motion; the slope type annular rolling bodies in the axial side are in rolling friction transmission, the slope type annular gear set (a right-angle gear set of a ring gear and a pinion, a common or universal ring gear, the pitch diameter and the tooth number of the ring gear are meshed with the pinions with various tooth numbers, namely a 6, 7, 8 and 9/39 ring gear) in the axial side is in gear friction transmission, and the central sun driven wheel is in two coupled motions of precession motion and rotation motion. The input side and the output side of the planetary reducer are exchanged to form a planetary speed increaser.
In an advantageous embodiment of the planetary gear reducer, the reducer or the speed increaser using the combination bearing and/or the transmission comprises the combination bearing, the stable transmission, the passive transmission and the axial retainer;
two axially opposite small gear sets (planet gears) on two sides of the sphere center of the combined bearing and/or the bearing of the transmission device are matched with a transmission rolling surface in the axial direction to run; the transmission rolling surface is constructed into an annular plane gear;
the tooth number of the annular plane gear teeth formed by the transmission rolling surfaces of the inner ring and the outer ring on one side of the sphere center in the axial direction is matched with the tooth number of the annular plane gear teeth formed by the transmission rolling surfaces of the inner ring and the outer ring on the other side of the sphere center of the pinion set to be matched with the pinion set to form tooth difference of the two sides;
the small gear set is formed by uniformly distributing axial retainers (planet carriers), the input shaft is tightly matched and connected with the inner diameter of the inner peripheral side of the axial retainer on one side, and the output shaft is tightly matched and connected with the inner diameter of the inner peripheral side of the axial retainer on the other side;
the outer ring at one side of the split outer ring (inner gear ring) is tightly matched and connected with the shell;
the annular plane gear on the outer ring consists of a flat ring, and a plurality of convex parts are arranged on the opposite surface of the teeth of the flat ring and matched with a plurality of concave parts on the axial side of the outer ring;
the input shaft directly gives a rotary input to one of the pair of axial retainers to drive the pinion set to rotate so as to roll along the annular plane gear of the outer ring at the static side, so that a sun gear (an inner ring) is driven to implement first-stage speed change, and meanwhile, the pinion set at the other side rotates to roll along the annular plane gear of the outer ring at the static side to drive the axial retainers so as to implement second-stage speed change of an output shaft connected with the retainers. The difference in teeth formed by the sets of pinions in the pair is such as to effect a variation in at least one kinematic parameter between drive and output.
The reduction gear or the speed increaser is designed as a passive transmission device, and the opposite of the small gear forms a conical uniform distribution with a transmission element in the passive transmission device.
The matching of the ring plane gear and the small gear set in the axial side is a right-angle gear set of the ring gear and the small gear, the tooth profile of the small gear forms a bevel gear and an asymmetric spherical gear, and the tooth profile of the ring gear is configured to the tooth profile of the small gear. In another arrangement, the cooperation of the ring face gear in the axial side with the pinion gear set is a crown gear having a 90 degree shaft angle and a pinion gear that is a spur gear.
In an advantageous embodiment, opposing planetary reducers and/or planetary speed increasers are used in combination with bearings and/or transmission reducers or transmission elements of the speed increasers, said planetary reducers and/or planetary speed increasers being driven by means of stationary, passive transmissions, axial cages and/or planetary trays,
the planetary reducer is tightly combined on a shell by a split internal gear ring sleeve (an annular gear or an axial raceway surface can be formed in the axial side of a split outer ring) in the axial direction, one side of the internal gear ring sleeve in the axial direction is formed by a plurality of elements on a power side which are equally combined on a first planetary element group on a tray, the other side of the internal gear ring sleeve in the axial direction is formed by a plurality of elements on a driven side which are equally combined on a second planetary element group on the tray, a connecting shaft on the power input side of a central sun gear is provided with a plurality of elements which are driven by external power and are between the driven side and the power output side, and the tray of opposite planetary transmission elements is supported and floated in the period by the power output shaft, the driven side, the internal gear ring sleeve and the power input side of the sun gear; when the input shaft drives the input side of the sun gear to rotate, the tray of the driven side second planetary transmission element is driven to rotate, so as to drive the output side first planetary transmission element to rotate and drive the output shaft connected with the tray to output power, and the opposite planetary transmission elements revolve along the central rotation axis along the track of the inner gear ring under the axial diameter ratio of each group of elements (the axial distance of one side element relative to the axial distance of the other side element or the tooth difference of the small gear group). The planetary transmission element group is arranged as follows: the rolling element is in rolling friction transmission in the axial side, the pinion gear group is in gear friction transmission in the axial side, and the central sun gear performs balanced rotary motion; the input side and the output side of the planetary reducer are exchanged to form a planetary speed increaser.
According to the design, at least two sun gears of the inner centers of the combined bearing and/or transmission device are oppositely and pairwise constructed to form a split type in the axial direction, namely, a group of transmission elements are added between the two sun gears, the outer spherical rolling surface of each group of sun gears in the radial direction and the inner spherical roller path of the ball row and the split inner gear sleeve form rolling motion and sliding motion, the auxiliary pair of transmission elements are matched on the two outer sides of the opposite split type sun gears, one split type inner gear sleeve externally surrounding the auxiliary pair of sun gears is provided with a through hole with a common rotating center line, the input side is closely matched and connected with the inner diameter of the sun gear on one side, the output side is closely matched and connected with the inner diameter of the sun gear on the other side, and the split type inner gear sleeves are axially connected by screws to form a whole body to form the speed reduction and/or speed increase transmission of the split type sun gears; the auxiliary pair of transmission elements is in the form of rolling elements, the split inner ring gear of the bearing and/or the device and the transmission rolling surface of the axial side of the sun gear are configured in the form of rolling elements, the two sides of the middle of the split sun gear form ring gears and/or transmission rolling surfaces, the central group of transmission elements are formed between the split sun gears as small gear sets and/or rolling elements, the central small gear sets and/or rolling elements are distributed uniformly as a common carrier plate, the central small gear sets and/or rolling elements form a configuration in which the steps of each transmission element are concentrically integrated in size, i.e. the stepped transmission elements form a large diameter end and a small diameter end, each gear of the small gear sets form gears with different tooth numbers at the large diameter end and the small diameter end, the ring gears of one side are in convex engagement with the teeth of the planetary transmission element, the ring gears of the other side of the planetary transmission element are uniformly distributed in a ring shape between the split sun gears, i.e. the ring gears of one side are in convex engagement with the ring gears of the split sun gear of the planetary transmission element in the axial direction; the clamping ring is arranged between the split type inner tooth ring sleeves and the radial outer diameter of the tray of the central transmission element group, the clamping ring forms two semicircular rings or movable connecting pieces which are opposite in the circumferential direction, the sections of the semicircular rings of the clamping ring form a T shape, the upper part of the T shape is an outer circumferential side, the lower part of the T shape is an inner circumferential side, the diameter of the outer circumferential side is larger than the outer diameter of the inner tooth ring sleeves, the inner circumferential side is positioned between adjacent parts of the inner tooth ring sleeves and is not in contact with each other, a plurality of screw through holes which are larger than screw holes on the inner tooth ring sleeves are arranged on the inner circumferential side and are correspondingly communicated with the screw holes on the inner tooth ring sleeves, the inner diameter surface of the inner circumferential side is in contact with the outer diameter surface of the tray for fastening, an elastic element is arranged between the inner diameter of the outer circumferential side and the outer diameter of the inner tooth ring sleeves to form two semicircular rings, and the semicircular rings are wave-shaped elastic steel sheets; two sides of the outer diameter of the outer periphery side form a slope shape, and the slope surface of the clamping ring is pressed by the axial movement of the sleeve of an external force to force the elastic steel sheet to deform, so that the inner diameter surface of the clamping ring is fixedly contacted with the outer diameter surface of the tray; wherein one force of the clamping ring forms each element of said set of central transmission elements spinning on the spindle; on the other hand, no external force exists, the elastic steel sheets enable the clamping ring to be radially separated from the outer diameter surface of the tray, the central transmission element group revolves, the force input side and the force output side synchronously rotate, and the central transmission element group revolves and rotates when the force output side has partial external force or is fixed; on the other hand, the tray can be provided with a connecting part which radially extends to the split internal gear ring sleeve and is not contacted with the adjacent part, and a screw on the internal gear ring sleeve passes through a screw through hole on the tray to fix the tray in the rotating direction and does not rotate; the central sun-split opposing reduction gear and/or speed increaser has a stepped gear design such that a transmission ratio of at least one order of magnitude is formed between the input side and the output side.
Drawings
The accompanying drawings illustrate some preferred embodiments of the invention, in which:
FIG. 1 is a front view of a stabilized transmission incorporating a ramped annular transmission element (bevel gear) of a bearing and/or transmission provided in accordance with a first embodiment of the invention;
FIG. 2 is a rear elevational view of a stabilized transmission incorporating ramped annular drive elements (bevel gears) of a bearing and/or transmission provided in accordance with a first embodiment of the present invention;
FIG. 3 is a cross-sectional view E-E of the stabilized drive according to FIG. 1;
FIG. 4 is a schematic illustration of the overall structure of a broken-away inner pinion gear set of a stabilized transmission incorporating ramped annular transmission elements of the bearing and/or transmission provided in accordance with the first embodiment of the present invention of FIG. 1;
FIGS. 5-7 are schematic illustrations of the overall structure of the disassembled inner axial pancake coils of a stabilized transmission incorporating the ramped annular transmission elements of the bearing and/or transmission provided in accordance with the first embodiment of FIG. 1;
FIG. 8 is a schematic illustration of the overall structure of the inner race of a stabilized transmission incorporating ramped annular transmission elements of the bearing and/or transmission provided in accordance with the first embodiment of FIG. 1;
FIGS. 9 and 10 are schematic illustrations of the overall structure of the disassembled split outer ring side of a stabilized transmission incorporating ramped annular transmission elements of a bearing and/or transmission according to the first embodiment of FIG. 1;
FIGS. 11 and 12 are schematic structural views of the other side of the disassembled split outer ring of a stabilized transmission incorporating ramped annular transmission elements of a bearing and/or transmission according to the first embodiment of FIG. 1;
FIG. 13 is a schematic view of a second embodiment of the present invention with the housing removed of the cycloidal reducer and/or speed increaser of a stabilized transmission incorporating ramped annular drive elements (bevel gears) of a bearing and/or transmission;
FIG. 14 isbase:Sub>A cross-sectional view A-A with the housing removed, according to FIG. 13;
FIGS. 15-17 are schematic illustrations of the disassembled inner cover wheels of the cycloidal reducer and/or speed increaser of the stabilized transmission incorporating ramped annular transmission elements of the bearing and/or transmission according to the second embodiment of the present invention;
fig. 18 and 19 are schematic structural views of the detached inner precession needle gears of the cycloid speed reducer and/or the speed increaser of the stable transmission device combining bearings and/or the slope type annular transmission element of the transmission device, provided by the second embodiment of the present invention;
FIG. 20 is a side view of a housing of a cycloidal reducer and/or speed increaser of a stable transmission incorporating bearings and/or ramped annular transmission elements of a transmission, provided in accordance with a second embodiment of the invention;
FIG. 21 is a cross-sectional view B-B of the belt housing of the cycloidal reducer and/or speed increaser according to FIG. 20;
FIG. 22 is a rear elevational view of the housing of the cycloidal reducer and/or speed increaser of the stabilized transmission incorporating ramped annular drive elements of the transmission and/or bearings provided in accordance with the second embodiment of the invention;
FIG. 23 is a front elevational view of a housing for a cycloidal reducer and/or speed increaser of a stabilized transmission incorporating ramped annular drive elements of a bearing and/or transmission provided in accordance with a second embodiment of the invention;
FIG. 24 is a perspective view of a housing for a cycloidal reducer and/or speed increaser of a stabilized transmission incorporating ramped annular drive elements of a bearing and/or transmission according to a second embodiment of the invention;
FIG. 25 is an exploded view of the housing of the cycloidal reducer and/or speed increaser of the stabilized transmission incorporating ramped annular drive elements of the transmission and/or bearings provided in accordance with the second embodiment of the invention;
FIG. 26 is another exploded view of the housing of the cycloidal reducer and/or speed increaser of the stabilized transmission incorporating ramped annular drive elements of the transmission and/or bearings provided in accordance with the second embodiment of the invention;
FIG. 27 is a side view of a stabilized transmission incorporating ramped annular transmission elements (asymmetric spherical rollers) of a bearing and/or transmission provided in accordance with a third embodiment of the invention;
FIG. 28 is a D-D cross-sectional view of the stabilizing transmission of FIG. 27;
FIG. 29 is a schematic illustration of the configuration of the needle hub of the broken inner pinwheel of the cycloidal reducer and/or speed increaser of the stabilized transmission combining bearings and/or ramped annular transmission elements of the transmission according to the fourth embodiment of the present invention;
FIG. 30 is a schematic illustration of the configuration of the broken inner pin gear teeth of the cycloidal reducer and/or speed increaser of the stabilized transmission incorporating ramped annular transmission elements of the bearing and/or transmission provided in accordance with a fourth embodiment of the invention;
FIG. 31 is a schematic illustration of the configuration of the disengaged inner driven wheels of the cycloidal reducer and/or speed increaser of the stabilized transmission incorporating ramped annular transmission elements of the bearing and/or transmission provided in accordance with a fourth embodiment of the invention;
FIGS. 32 and 33 are schematic views of the unraveled inner precessional cycloidal gears of a cycloidal reducer and/or speed increaser of a stabilized transmission incorporating ramped annular transmission elements of a bearing and/or transmission according to a fourth embodiment of the present invention;
FIG. 34 is an exploded pictorial illustration, without the housing, of a cycloidal reducer and/or speed increaser of a stabilized transmission incorporating ramped annular drive elements (asymmetric spherical rollers) of a bearing and/or transmission according to a fourth embodiment of the present invention;
FIG. 35 is a front elevational view of the housing of the cycloidal reducer and/or speed increaser of the stabilized transmission incorporating ramped annular drive elements of the transmission and/or bearings provided in accordance with the fourth embodiment of the invention;
FIG. 36 is a side elevational view of the belt housing of the cycloidal reducer and/or speed increaser of the stabilized transmission incorporating ramped annular transmission elements of the transmission and/or bearings provided in accordance with the fourth embodiment of the invention;
FIG. 37 is a C-C cross-sectional view of the cycloidal reducer and/or speed increaser according to FIG. 36;
FIG. 38 is a rear elevational view of a housing for a cycloidal reducer and/or speed increaser of a stable transmission incorporating bearings and/or ramped annular drive elements of the transmission, provided in accordance with a fourth embodiment of the invention;
FIG. 39 is an exploded view of the housing of the cycloidal reducer and/or speed increaser of the stabilized transmission incorporating ramped annular drive elements of the bearing and/or transmission provided in accordance with the fourth embodiment of the invention;
FIG. 40 is a front view of a cage and/or a planetary tray carrier of a combination bearing and/or transmission provided in accordance with a fifth embodiment of the present invention;
FIG. 41 is a sectional view taken along line G-G of the cage and/or the planet carrier according to FIG. 40;
FIG. 42 is a rear elevational view of the cage and/or the planet carrier of the combination bearing and/or transmission provided in accordance with the fifth embodiment of the present invention;
FIG. 43 is a perspective view of a cage and/or a planetary tray carrier of a combination bearing and/or transmission provided in accordance with a fifth embodiment of the present invention;
FIG. 44 is a front view of a cage and/or a planet carrier with rolling elements and/or gears removed of a combination bearing and/or transmission provided in accordance with a fifth embodiment of the present invention;
FIG. 45 is a rear view of a cage and/or a planetary carrier of a combination bearing and/or transmission with rolling elements and/or gears removed and provided in accordance with a fifth embodiment of the present invention;
FIGS. 45a and 45b are front and rear views of a cage and/or a planetary tray carrier of a combination bearing and/or transmission provided by a fifth embodiment of the present invention with mandrels removed;
FIG. 45c is a partial T-view of the cage and/or the planet carrier according to FIG. 45a, with the mandrel removed;
FIG. 45d is a partial Y-view of the cage and/or the planet carrier according to FIG. 45b, with the mandrel removed;
45e and 45f are spindle views of a cage and/or a planetary tray carrier of a combination bearing and/or transmission provided by a fifth embodiment of the invention;
FIG. 46 is a front view of a reduction gear and/or a speed increaser of a combined bearing and/or transmission according to a sixth embodiment of the invention, from which the inner race is directly connected to the input shaft to form a stable transmission according to another design concept;
FIG. 47 is a side view of a reduction gear and/or a speed increaser of a combined bearing and/or transmission according to a sixth embodiment of the present invention, from which the inner race is directly engaged with the input shaft to form a stable transmission according to another design concept;
FIG. 48 is a cross-sectional H-H view of the retarder and/or speed increaser according to FIG. 46;
FIG. 49 is an exploded view of a reduction and/or speed increaser incorporating bearings and/or a transmission according to a sixth embodiment of the invention;
FIG. 50 is a rear elevational view of a bicycle incorporating a bearing and/or transmission provided in accordance with a seventh embodiment of the present invention;
FIG. 51 is a side elevational view of a bicycle incorporating a bearing and/or transmission provided in accordance with a seventh embodiment of the present invention;
FIG. 52 is a top plan view of a bicycle incorporating a bearing and/or transmission provided in accordance with a seventh embodiment of the present invention;
FIG. 53 is a perspective view of a bicycle incorporating bearings and/or transmissions in accordance with a seventh embodiment of the present invention;
FIG. 54 is another perspective view of a bicycle incorporating bearings and/or transmissions provided in accordance with a seventh embodiment of the present invention;
FIG. 55 is a side elevational view of a split sun-wheel opposed speed reducer and/or opposed speed increaser incorporating a bearing and/or transmission in accordance with an eighth embodiment of the present invention;
FIG. 56 is a front elevational view of a split sun-wheel contra-mounted speed reducer and/or opposed speed increaser incorporating bearings and/or a transmission in accordance with an eighth embodiment of the present invention;
FIG. 57 is a cross-sectional S-S view of the opposed reduction and/or opposed speed increaser according to FIG. 56;
FIG. 58 is a partial view Q of the opposed reduction gear and/or opposed speed increaser according to FIG. 57;
FIG. 59 is an exploded view of a split sun-wheel contra-mounted speed reducer and/or contra-mounted speed increaser incorporating bearings and/or transmissions according to an eighth embodiment of the present invention;
Detailed Description
It should be noted that, in case of conflict, the embodiments and features of the embodiments in the present application may be combined with each other throughout the present application, and features and functions of each embodiment and assemblies are mentioned in one place and should be understood in other embodiments; it is convenient to explain that the left-right relationship is shown for the embodiment of the drawings, and the left-right relationship can be mutually converted by rotating the embodiment by 180 degrees for the convenience of description. The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
In the embodiment of the invention, the invention provides a bearing combining a bearing and a precession effect, a stable or passive or active transmission device, an axial retainer and/or a planetary tray, and conversion and utilization of the transmission device, wherein the retainer is a radial ball ring type bowl hole retainer, an axial ball hole retainer, an axial triangular hole retainer, an axial annular window type retainer and an axial annular window type retainer, and different arrangement forms of the axial annular window type retainer for rollers cannot be unclear when the retainer is used in different devices; wherein like numerals in the figures refer to like features of the combination bearing and/or transmission, wherein the ramped annular transmission elements may also be referred to as ramped circumferential rolling elements. 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.
For the purposes of promoting an understanding of the principles of the disclosure, reference will now be made to the embodiments illustrated in the drawings and described in the following written specification. It will nevertheless be understood that no limitation of the scope of the disclosure is thereby intended. It is also to be understood that the present disclosure includes any alterations and modifications to the illustrated embodiments and includes further applications of the principles of the disclosure as would normally occur to one skilled in the art to which the disclosure relates.
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be obtained by a person skilled in the art without making any creative effort based on the embodiments in the present invention, belong to the protection scope of the present invention.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the invention. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof, unless the context clearly indicates otherwise.
The relative arrangement of the components and steps, the numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present invention unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate. Any specific values in all examples shown and discussed herein are to be construed as exemplary only and not as limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, further discussion thereof is not required in subsequent figures.
In the description of the present invention, it is to be understood that the orientation or positional relationship indicated by the directional terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal" and "top, bottom", etc., are generally based on the orientation or positional relationship shown in the drawings, and are used for convenience of description and simplicity of description only, and in the absence of any contrary indication, these directional terms are not intended to indicate and imply that the device or element so referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore should not be considered as limiting the scope of the present invention: the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself.
For ease of description, spatially relative terms such as "over … …", "over … …", "over … …", "over", etc. may be used herein to describe the spatial positional relationship of one device or feature to another device or feature as shown in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device in the figures is turned over, devices described as "above" or "on" other devices or configurations would then be oriented "below" or "under" the other devices or configurations. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may be otherwise variously oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
First embodiment
Fig. 1 to 12 show a first embodiment of a compound bearing and/or stabilising transmission 1, the transmission elements of the ramped ring gear members 141,142 of the transmission 1 being shown as pinion sets, the pinion sets 141,142 corresponding in design to right angle sets of axial side ring gears 121,122, 133,134 with pinions, a common or common ring gear having a pitch diameter and teeth meshing with pinions of various teeth, i.e. a ring gear of 6, 7, 8 and 9/39 (where the numbers refer to the numbers of teeth of the gears) is provided, e.g. each pair of opposed pinion sets is formed by several gears of 6, 7, 8 and 9 (where the numbers refer to the numbers of teeth of the gears) distributed around the ring, i.e. forming ramps; the opposing side pinion set 141 is configured to facilitate rolling and/or gearing of the ring gear surfaces 121,122, 133,134 in the axial sides of the inner and outer races relative to the other side pinion set 142.
The combined bearing and/or stabilizer drive 1, whose overall construction comprises the combination of inner and outer races 120,100 and ball rows 907,908 and ramped annular drive elements 141,142, is integrally connected by screws 91. Wherein their configuration:
and an inner ring 120 having a circular ring shape with a center thereof extending therethrough, and having an outer spherical raceway 909 formed on a radially convex spherical surface of the circular ring shape, wherein the distance from the bearing center to the left and right sides in the axial direction of the circular ring-shaped inner ring is equal and/or the distance from the left and right sides to the bearing center is offset. The inner ring has in its annular shape a first raceway facing generally in one axial direction and a second raceway 122 facing in the opposite axial direction; and/or the inner ring has in its annular shape a first raceway 121 facing in one axial direction and a second raceway 122 facing in the opposite axial direction; and/or the inner ring has in its annular shape a first raceway facing substantially in one axial direction and a second raceway facing substantially in the opposite axial direction; and/or the inner ring has in its annular shape a first raceway 121 facing in one axial direction and a second raceway facing substantially in the opposite axial direction.
And/or the left and right raceways of the inner ring in the annular axial direction of the inner ring are parallel annular plane raceways, and the concave, convex, concave and convex thrust angular contact annular spherical raceways and/or conical surface raceways and/or spherical raceways.
And/or the two side raceways 121 and 122 opposite to the annular first and second raceways in the axial direction are formed into thrust angular contact conical surface raceways on one side and axially contacting annular planar raceways on the other side, and/or one side of the annular left and right opposite side raceways in the axial direction is formed into thrust angular contact annular spherical raceways on the other side and axially contacting annular spherical raceways on the other side, and/or the annular first and second raceways in the axial direction are both formed into thrust angular contact conical surface raceways and/or thrust angular contact annular spherical raceways and/or spherical raceways.
A plurality of blind holes for retaining the solid lubricant are formed in the radially outer spherical raceway surface 909 and the axially first and second raceway surfaces of the inner ring.
The idea of the invention is to arrange the outer ring 100 such that,
the outer ring 100 further comprises a first split outer ring 101 and a second split outer ring 102, which are arranged in a cover ring shape, wherein the outer diameter of the outer ring on one side of the first and second split outer rings is slightly smaller than the outer diameter of the outer ring on the other side of the first and second split outer rings, and/or the outer diameters of the outer rings on both sides of the first and second split outer rings are the same; and the outer ring with the large outer diameter on one side of the combined outer ring is in interference fit with the bearing box, and/or the outer rings with the same outer diameters on the two sides of the combined outer ring are in interference fit with the bearing box.
The cross section of the combination of the first outer ring 101 and the second outer ring 102 in the cover ring shape is substantially in a shape of a Chinese character 'ao', each part of the outer ring in the cover ring shape forms three steps, the first step of the three steps is the middle part of the combination of the first outer ring and the second outer ring in the axial direction of the bearing, the second step and the third step of the three steps extend towards the direction of the rotation axis in the bearing, each step of the outer ring forms two annular end faces in the axial direction and the radial direction, the end face in the axial direction of the first step of the combination of the first outer ring and the second outer ring is the abutting part 108 of the two outer rings and the first inner spherical raceway 905 in the radial direction, the end face in the axial direction of the second step is a chamber (first spherical inner spherical raceway) connecting the end face in the radial direction of the first step and forming the combination of the first step, the end face in the radial direction of the second step forms a spherical second inner spherical raceway 906 having a shape and a diameter equal to the outer spherical raceway 909 in the radial direction of the inner ring, the inner face in the axial direction of the third step is a radial side connecting the radial direction of the second outer ring and can form a ring raceway in the axial direction and a third inner ring and a third step and a third inner raceway; the outer end face of the third step in the axial direction is an annular end face connected with the third step in the radial direction and forms an outer annular plane, and the outer portion of the first step in the radial direction is the outer diameters of the first outer ring and the second outer ring and is connected with the outer annular plane of the third step in the axial direction.
The end faces of the abutting parts 108 of the first outer ring and the second outer ring are positioned on the radial extension line of the bearing spherical center and/or are offset relative to the radial extension line of the bearing spherical center, the end faces of the abutting parts 108 are contacted or not contacted, and the distances from the third ball tracks of the first outer ring and the second outer ring to the bearing spherical center are equal and/or unequal.
The first spherical inner spherical raceway 905 of the first step of the combined three-step steps of the first outer ring and the second outer ring has a larger diameter than the outer spherical raceway 909 of the inner ring, and a plurality of ball rows 907,908 are axially distributed in the space between the first spherical inner spherical raceway 905 and the outer spherical raceway 909 of the first step; guided by an axially-distributed cage and allowed to freely move in a point-contact multi-angle manner between the raceways, each ball diameter of each pair of ball rows on the left and right sides of the axially-distributed ball rows 907,908 in the left and right hemispherical spaces is the same, wherein the at least one pair of ball rows are distributed on the left and right sides of a radial extension line of the bearing center. The pockets and the connecting ribs of each row of the retainer arranged around the spherical contour face towards the sphere center, wherein the plurality of pockets uniformly distributed in the circumferential direction of the retainer contain a plurality of balls to form a bowl shape, the bottom of the bowl is provided with an opening, and the diameter of the opening of the bowl surface with the large diameter of the bowl-shaped pocket is slightly larger than that of the balls and faces towards the outer ring. The rows of balls 907,908 are placed in the first step cavity spherical raceway of the outer race during assembly and these bowl-shaped pockets retain the balls against loss.
The second inner spherical raceway 906 of the second step of the three-step steps of the first and second outer rings extends to the raceway 909 of the outer spherical surface of the inner ring, the diameter of the second inner spherical raceway 906 of the combined first and second outer rings, which passes through the center of the sphere, is the same as the diameter of the outer spherical raceway surface 909 of the inner ring, and the second inner spherical raceway and the outer spherical raceway surface form sliding motion.
The third steps of the three steps of the first outer ring and the second outer ring are extended to form a left raceway and a right raceway (transmission rolling surfaces of the first raceway and the second raceway) which are separated to partially cover the axial direction of the inner ring, the axial inner side end surface of the third step forms transmission rolling surfaces 133 and 134 of an axial third raceway, the transmission rolling surfaces and the transmission rolling surfaces are different in configuration and correspond to the axial two raceways 121 and 122 of the inner ring, second rolling bodies (transmission elements) are held by an axial retainer and roll and/or transmit among the raceways in the axial direction, and the axial outer side end surface of the third step forms a circular ring-shaped plane. A thrust angular contact conical surface raceway is arranged on one side of the axial third raceway, an axial contact ring planar raceway is arranged on the other side of the axial third raceway, and/or a thrust angular contact annular spherical raceway is arranged on one side of the axial third raceway, an axial contact annular spherical raceway is arranged on the other side of the axial third raceway, and/or thrust angular contact conical surface raceways are arranged on two side faces of the axial third raceways of the first outer ring and the second outer ring and/or thrust angular contact annular spherical raceways are arranged on two side faces of the axial third raceway of the first outer ring and the axial third raceway of the second outer ring; and/or two side surfaces of the axial third ball tracks of the first outer ring and the second outer ring are respectively a parallel annular plane ball track, a concave, convex and concave-convex annular ball track or a conical surface ball track and/or a spherical ball track.
The distance from the drive running surface 133 of the axial third raceway of the first outer ring to the first drive running surface 121 in the axial direction of the inner ring is equal and/or unequal to the distance from the drive running surface 134 of the axial third raceway of the second outer ring to the second drive running surface 122 in the axial direction of the inner ring, and the raceways in the axial direction are configured as raceway contact surfaces in the shape of the second rolling elements 141,142 (drive elements).
The first step inner cavity spherical raceway 905 and the second step inner spherical raceway 906 are upper and lower spherical raceways of a step with the same spherical center, and the axial third raceway is a cover ring shape, and the section of each side outer ring is generally L-shaped.
The peripheries of the annular planes on the axial outer sides of the first outer ring and the second outer ring are oppositely provided with a plurality of staggered connecting holes 9 (screw holes), the connecting holes penetrate through the axial abutting surface of the first step from the annular plane to form threaded counter bores on the opposite surface, elastic elements are sleeved on the heads of the connecting screws, and a certain axial pretightening force is applied through the connection of the connecting screws to connect the outer ring 100, the plurality of ball rows 907 and 908, the pair of second rolling bodies 141 and 142 in the axial direction and the inner ring 120 into a whole.
In an advantageous design scheme, the outer ring on one side with a large outer diameter of the outer ring is in interference fit with the bearing box, a plurality of connecting screws 91 on the left and the right are respectively connected with the first outer ring and the second outer ring on the left and the right in a two-way mode, elastic elements are sleeved on screw caps of the screws to apply a pretightening force, and the elastic elements are added on the screw caps to automatically tighten the connection between the first outer ring and the second outer ring on the left and the right and the connection between the multiple rows of balls, the second rolling element (transmission element) and the inner ring. After the bearing runs and wears, the first outer ring, the second outer ring, the rows of balls, the second rolling body and the inner ring are pre-tightened in the opposite direction relative to each other in the axial direction for the freedom degree from the clearance, the outer ring at the other side with the small outer diameter is automatically and flexibly pre-tightened, particularly, the outer ring is pre-tightened through a proper spring mechanism, the bearing is always in the gapless flexible automatic pre-tightening, and the combined bearing and/or the transmission device runs accurately and stably.
In an advantageous embodiment, the distance from the third axial raceway of the first outer ring to the first axial raceway of the inner ring is equal and/or unequal to the distance from the third axial raceway of the second outer ring to the second axial raceway of the inner ring, and the distance is configured to arrange the second rolling elements and to be held by the cage in the axial direction at the contact surface of the raceway configuration of the second rolling elements, forming a circumferential moment of the elastic element on the annular cage such that the second rolling elements are tangent to the raceway contact surface and roll.
The drive elements of the ramp-like ring drive elements of the illustrated stabilized drive 1 can also be in the form of tapered rollers, tapered and cylindrical roller combinations, as shown in fig. 48 and 49, the asymmetrical spherical roller pattern 28 has a display, the rolling elements such as balls are formed in combination, i.e. they form ramp-like drive running surfaces and are paired opposite one another in the axial direction, and the drive running surfaces in the axial direction of the inner and outer rings are configured in the form of rolling elements; where their transmission is a rolling friction transmission motion. The rolling friction transmission of the stable transmission 1 is always kept in contact by the force of the elastic elements on the screw in one axial direction and the force of the elastic elements on the cage in one radial direction (shown in fig. 43), so that the transmission elements do not come into contact.
The gearing elements of the ramp-type ring gearing of the illustrated stable gearing 1 are shown as sets of pinions 141,142, the ring gears 133,134 shown in the axial sides of the outer ring of the device being formed by separate flat rings 131,132 forming one side ring gear 133,134 and the other side plurality of protrusions 112, the flat rings 131,132 forming the plurality of protrusions 112 in mating connection with the plurality of recesses 111 formed in the axial sides of the split outer ring.
The stable transmission 1 is mounted in a manner such that, first, the outer ring 100 on one side is laid on a table, the convex portions 112 of the flat rings 131,132 are fitted into the concave portions 111 on the axial side of the outer ring 100, second, the pinion gear sets 141,142 are mounted on the ring gears 133,134 of the flat rings, third, the ball rows 907,908 are fitted into the first stepped spherical raceway 905 of the outer ring, fourth, the inner ring 120 is fitted into the second stepped spherical raceway 906 and the ball rows 907 of the outer ring, fifth, the shaft hole of the inner ring 120 is penetrated with a T-shaped round bar and is reversely fitted into the element of the outer ring 100 which is partially fitted, and sixth, the split outer ring is connected with the screw 91. Otherwise, the rolling bodies are arranged, and the first step is eliminated.
And a space for accommodating a plurality of rows of balls is arranged between the first step inner cavity spherical raceway combined by the first outer ring and the second outer ring and the outer spherical raceway of the inner ring. The first inner cavity spherical raceway and the outer spherical raceway can accommodate multiple rows of balls and enable the balls to freely roll at multiple angles at the point contact of the two spherical raceways, in order to keep the relative positions of the multiple rows of balls, a pocket of a retainer of the spherical ring surface is added, the pocket of the retainer deflects towards the center of a sphere relative to the balls and holds the balls and is matched with an outer ring to prevent loss and keep the balls, the retainer is matched with a left outer ring and a right outer ring to enable the two rows of ball ring surfaces to be uniformly distributed at axial intervals, and the relative position of each ball of each row of balls can be ensured not to change in the rolling process; the retainer adopts a polytetrafluoroethylene retainer, has a certain self-lubricating function and can lubricate the balls, adopts a ball ring structure, and pockets uniformly distributed on the retainer keep the balls in the process of the precession movement of the bearing. After the first outer ring and the second outer ring are combined and connected through the screw cap head matched with the pre-tightening of the spring, the outer ring on one side with a large outer diameter can only be matched with the bearing box, and the outer ring on the other side with a small outer diameter can only be tensioned in a gapless way through the flexible axial direction of the spring on the screw; each row of balls are closely tangent to the inner spherical raceway and the outer spherical raceway, a pocket of the retainer, which is deviated to the center of the sphere, is matched with the spherical raceway of the inner cavity of the first step of the outer ring to keep the balls from being lost, and the pocket only controls the relative position of each ball but depends on the lateral angle of the ball row.
The axial ring plane raceways of the third steps of the first and second outer rings are arranged to correspond to the axial ring plane raceways of the first and second raceways of the inner ring, and the axial distances between the axial ring plane raceways are equal (here and below, the ramp type circumferential rolling elements or ramp type annular transmission elements of the tapered roller and cylindrical roller combination are described) as shown in fig. 48 and 49, which show transmission in the transmission of rolling motion friction.
An axial pair of ramp-type circumferential rolling elements are disposed between the raceways at an axial distance (space) between the inner and outer races. The ramp-type circumferential rolling elements are combined into each row by two cylindrical rollers and a plurality of tapered rollers. The two cylindrical rollers at two ends of each row of diameter line divide two semicircles at two sides into tapered rollers, the large-diameter end surfaces of the rollers uniformly distributed on one semicircular side of the tapered rollers face the circle center of the retainer and the rotation axis of the retainer, the small-diameter end surfaces of the tapered rollers uniformly distributed on the other semicircular side face the circle center of the retainer and the rotation axis of the retainer, and each tapered roller and the two cylindrical rollers on the ring circumference of the tapered rollers form two opposite plane rolling surfaces with an angle slope, namely the angle range of the opposite rolling surfaces formed by each row of slope type ring rolling elements is 1-10 degrees. The pair of ramped circumferential rolling elements are disposed in the bearing such that the small-diameter tapered rollers of the left side transmission element are parallel in planar space with respect to the large-diameter tapered rollers of the right side transmission element and the left and right cylindrical rollers are opposed to each other.
The circumferential rollers formed by the pair of ramp-type circumferential rolling elements are retained by an annular window-type cage (a manner of retaining the cage is described herein, not shown), and pockets on the annular outer peripheral side of the cage are configured in the shapes of tapered rollers and cylindrical rollers. Meanwhile, the elastic elements are arranged in the pockets and abut against the large-diameter end face of each tapered roller, so that the elastic elements are distributed on the outer periphery (on the large-diameter tapered roller) of each semicircle, and the elastic elements are distributed on the inner periphery (on the small-diameter tapered roller) of each semicircle. Meanwhile, the elastic element is formed into an H-shaped arc-shaped steel sheet, a spring is connected in an arc concave part of the H-shaped arc-shaped steel sheet, grooves at two ends of the H-shaped steel sheet are pre-pressed and inserted into the window-type pocket to be movably connected, and the other end of the spring is abutted to the radial end part of the inner periphery or the outer periphery of the window-type pocket. The tapered roller is clamped in the pocket, one end of the tapered roller is abutted to the convex part of the arc-shaped steel sheet to enable the spring to deform, and the other end of the tapered roller is abutted to the inner periphery or the outer periphery of the window-type pocket. The section of the annular retainer forms a T-shaped inner peripheral side and an outer peripheral side (the upper part of the T shape is the inner peripheral side, the lower part is the outer peripheral side), the outer diameter of a ring part of the inner peripheral side of the retainer (the inner peripheral side of the upper part of the T shape) is slightly smaller than that of a through hole of the outer ring, one side of the ring part extends into one part of the through hole, and the other side of the ring part extends to the axial end face of the inner ring to leave a certain gap. And the ring portion of the cage is constructed at the same angle (gradient) as the ramp circumferential rolling elements. An elastic rubber seal ring is sleeved on the outer diameter of the ring part of the retainer (the outer diameter of the inner peripheral side of the T-shaped upper part) and is abutted against the axial end faces of the inner ring and the outer ring to form sealing. And a pair of ramp circumferential rolling elements are identical.
The outer diameters of the outer rings of the combined bearing and/or the transmission device 1 are different or the same and are in interference fit with the bearing box, a single-side first outer ring (with a large outer diameter) is in interference fit with the bearing box according to a use scene, a second outer ring (with a small outer diameter) can be automatically flexibly tensioned axially, and the combined bearing and/or the transmission device is a torque applied by an elastic element matched with a screw cap of a screw. According to the principle of general manufacturing, the distance from the center of the ball of the bearing to the axial sides of the two sides is equal.
The distance of spring deformation of the elastic element formed on the retainer in one direction is matched with the distance of the spring deformation of the retainer in one direction, which is used for a certain time according to the operation of the combined bearing and/or transmission device 1, the ring part on the retainer is abutted against the shaft hole of the outer ring to enable the tapered roller to move towards the direction of the small-diameter end face, and meanwhile, the elastic elements of the screws on the first outer ring and the second outer ring are automatically tensioned in a two-way mode in the axial direction. The combined bearing is always in close fit with the first and second outer rings and the plurality of first ball rows of the assembly, and the pair of slope type circumferential rolling elements and the inner ring in operation. This design concept may be combined differently throughout the following embodiments.
In operation of the combined bearing and/or transmission 1, the free multi-angular point contact rolling movement of the ball rows 907,908 in the first step cavity spherical raceway 905 of the first and second outer races and the outer spherical raceway 909 of the inner race is controlled by the angular disposition of a pair of ramped circumferential rolling elements which cooperate with respect to each other to define an angle α between the central axis of the outer race and the central axis of the inner race, and the tangential line contact rolling of the pair of ramped circumferential rolling elements between the axial ring plane raceways of the inner and outer races is also effected by the moment of the resilient elements on the cage. In the sliding friction motion of the second stepped inner spherical raceway 906 of the existing outer ring and the outer spherical raceway 909 of the inner ring, the axial distance of contact of the raceway surfaces of both of them plays a role in the axial transition of the ball row in the bearing and the ramp-type circumferential rolling element and the whole bearing is stably matched, and the axial angle of the axial side of the contact of the raceway surfaces of both of them during precession is in contact angle 360 ° rotation during the motion (the opposite contact raceway surfaces during precession are formed with contact and without contact on both sides of one side of the bearing). At least one pair of ball rows 907 and 908 are distributed at two sides of the axial direction of the bearing ball centers of the inner spherical raceway 906,905 and the outer spherical raceway 909 and are larger than the distance from the first stepped inner cavity spherical raceway 905 to the outer spherical raceway 909, so that the free rolling motion is firstly performed for a certain time, then the sliding motion of the second stepped inner spherical raceway 906 and the outer spherical raceway 909 is added, and the pair of ball rows are tangent between the inner spherical raceway and the outer spherical raceway by the axial moment of the spring on the screw 91. When the deflection angle of the inner ring is relatively large, the lateral angle of the outer ball raceway surface 909 forming the inner ring is separated from the second step inner ball raceway surface 906 and part of the balls are separated, and the balls are kept from being lost by matching a pocket of the retainer deviated to the center of the ball and the first step inner cavity ball raceway 905 of the outer ring.
The sliding motion can bring a large amount of heat and friction, different design ideas are adopted, the diameter of each ball of the ball rows is slightly larger than the distance from the spherical raceway of the inner cavity of the first step to the spherical outer raceway, and therefore the ball rows and the slope type circumferential rolling elements are firstly constructed to be installed together and connected with the rolling motion in the bearing. After the rolling motion pattern (point and line contact motion) undergoes deformation or wear with approximately half the torque, the sliding motion pattern (surface contact motion) adds to the deformation or wear with approximately half the torque.
The principle and function of the steady precession of the combined bearing and/or transmission 1 is taught here: the central axis of the inner ring 120 and the central axis of the outer ring 100 in fig. 3 are inclined by an angle α ° relative to each other due to the angle (slope) of the arrangement of the pair of ramped circumferential rolling elements 141,142, and the inner ring or the outer ring is driven to rotate in a fixed axis manner, and a precession (nutation ) motion effect occurs in the opposite direction. One part rotates, and the high-speed rotation motion of the pair of slope type circumferential rolling elements drives the other part to rotate in the opposite direction and simultaneously carry out precession motion. If one side of the outer ring rotates around the self rotating shaft, the central axis of the outer ring revolves and precesses around the central axis of the inner ring at an angle of alpha degrees, and rotates and precesses around the spherical center of the bearing at 360 degrees, the precession motion is stable, the bearing is subjected to a second moment (the friction force of an external force and the centrifugal force) during operation, and the abrasion time of the rolling friction motion of the rolling bodies is different. However, the elastic elements in the bearings always exert a flexible pretension of the axial force and the radial-side moment, so that the phenomenon of rolling motion dislocation cannot occur. Suitable elastic elements are used depending on the magnitude of the second torque.
The angle of the slope type circumferential rolling elements (the slope angle of each row of rollers is set) is also limited, the central axis of the inner ring and the central axis of the outer ring are relatively inclined by an angle alpha degrees, if the inner ring rotates to drive the outer ring to rotate and precess in the opposite directions, according to the angle (the slope is high and low) of the slope type circumferential rolling elements, the precession speed of the outer ring is high (the angular speed is high) when a small angle is designed; when a large angle is designed, the precession speed of the outer ring is slow (angular speed is slow). The transmission ratio which brings effect by the inherent movement speed ratio is used in the nutation transmission mechanism (a face gear arranged on the outer end face of the outer ring on one side of the precession outer ring in the axial direction is matched in the transmission mechanism relative to the other side face gear).
The dynamic characteristics (principle) brought by the stable precession motion are used in the relevant mechanical fields, such as driving an inner ring to rotate, driving an outer ring to precess (whirl, nutation) to move, and can be used in a swing type crusher, a helicopter double-blade rotor mechanism (single shaft, coaxial), a whirl bit for underground drilling, a swash plate type axial propulsion system in a plunger pump mechanism, a deflection component of a swing type electric tool or a bit used in an electric tool (inner ring to rotate, outer ring to revolve to expand drill or vice versa outer ring to rotate, inner ring to revolve to expand drill), such as an internal combustion engine driving motion, an outer ring precession driving inner ring to rotate (instead of a swash plate type reciprocating mechanism engine), such as a mechanism of a wind power equipment (one of which is connected with an outer ring to advance at a low speed and an output shaft is connected with an inner ring to rotate at a high speed), and the other of which a rotating shaft of the wind power equipment currently used is connected with an inner ring and a propeller hub connected with an outer ring.
The different steady transmissions 1 according to the design have two forms of rolling and sliding movement:
first, rolling → rolling plus sliding, fig. 1 to 12 are assembled as above, with the inner spherical raceways of the opposing second steps of the first and second outer races of the outer race having a diameter through the center of sphere equal to the diameter of the outer spherical raceway of the inner race; the left and right rows of balls of the radial extension line on the ball center are axially arranged oppositely left and right, and the diameter of each ball of each row of balls opposite left and right is slightly larger than the distance from the first step inner cavity spherical raceway to the outer spherical raceway. Then according to the condition of the axial clearance between the left outer ring and the right outer ring, the screw applies a pretightening force to adjust the moment of the elastic element, so that the purpose of accurately adjusting the clearance between the left and right rows of balls to the first step inner cavity spherical raceway and the outer spherical raceway can be achieved. Whilst the ramped circumferential rolling elements are configured to cooperate together with the distance measured between the axial ring gears of the ball train in the bearing. When the raceways of the outer ring, the multiple rows of rolling bodies and the inner ring and the rolling bodies are in motion fatigue wear, the diameters of the three are changed, the outer diameter of a left outer ring of the outer ring combination is slightly larger than the outer diameter of a right outer ring, a first outer ring with a large outer diameter is in interference fit with a bearing box through the flexible combination of the two outer rings, a second outer ring with a small outer diameter is automatically and flexibly pre-tightened, and an elastic element on a screw head has elastic force to enable the outer ring, the multiple rows of rolling bodies and the inner ring to be connected together all the time. Through the adjustment, firstly, the rolling contact of the multiple rows of rolling bodies is used, and on one hand, the gaps between the multiple rows of rolling bodies and the inner ring and between the multiple rows of rolling bodies and the left outer ring and between the multiple rows of rolling bodies and the right outer ring can be adjusted automatically through the torque of the pretightening force of the elastic element of the bolt. After the left and right rows of rolling bodies in the axial direction are subjected to motion fatigue wear, the second step inner spherical raceway and the second step outer spherical raceway perform sliding motion. On the other hand, the rolling friction of the original bearing is changed into the combination of the rolling friction and the sliding friction of the 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 after the sliding motion in flexible fit provides approximately half of torque, the sliding friction coefficient does not generate severe friction, meanwhile, the rolling friction coefficient 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, the sliding and rolling move simultaneously, and the diameters of the first step inner cavity spherical raceway of the outer ring and the outer spherical raceway of the inner ring can also be set to be the same as the ring spherical inner and outer diameters of the left and right rows of balls (the diameter of each ball of the left and right rows of balls is equal to the distance from the first step inner cavity spherical raceway to the outer spherical raceway). The diameters of the second inner spherical raceway of the second step of the outer ring and the outer spherical raceway of the inner ring are the same, the outer ring, the two rows of balls distributed in the left and right spherical spaces and the inner ring are concentric and tangent, and meanwhile, the slope type circumferential rolling elements are configured to be matched with the distance measured between the axial ring gears of the ball rows in the bearing. A pretightening force is applied to a plurality of bolts opposite to each other of the left outer ring and the right outer ring, so that the elastic element has certain torque, and the outer ring, the rows of rolling bodies and the inner ring are connected into a whole to slide and roll and move simultaneously.
Second embodiment
Fig. 13 to 26 show a second embodiment of a cycloidal reducer/cycloidal gearbox 200 using the stationary transmission 1.
The illustrated cycloidal reducer or speed increaser 200 includes: first and second rolling bearings 201,202, a cover wheel 203, a precession pin gear 210, a transmission 1, a rigid ball 207, an input shaft 206 and a housing 280; the steady-state transmission in the cycloidal reducer/cycloidal increaser 200 is represented in the figures by ramped annular drive elements or ramped circumferential rolling elements as ring gears in the axial sides of the mating pinion sets; the slope type annular transmission element or slope type circumferential rolling element can form a transmission element and a ball which are combined by a tapered roller, an asymmetric spherical roller, a cone and a cylinder, and the transmission rolling surface movement of the transmission element at the axial side is contact friction movement; in a further embodiment, the transmission element is formed as a pinion gear train and an intersecting shaft transmission, the transmission running surfaces of which are configured as the tooth profiles of the gears: the transmission surface of the transmission element pinion set on the axial side moves into tooth-tooth contact friction motion;
the carrier for the pinion set is described in other embodiments below. The cage of the rolling element can take the form described above and can also be described in the following exemplary embodiments.
The precession needle gear 210 is arranged into a conical body 205, a needle groove is formed in the periphery of the conical body 205, the needle teeth 204 are movably matched in the needle groove, the precession needle gear 210 is sleeved on the outer ring 102 on one side of the transmission device 1 and fixedly connected with the outer ring, and a pin 2088 is inserted into matching grooves 1020 and 2050 of the precession needle gear and the outer ring;
the inner periphery of the cover wheel 203 is provided with internal teeth 2031, the axial center of the cover top is provided with an output shaft 2032, the inner bottom of the axial center of the cover wheel is provided with a spherical concave part 2030, and the outer periphery is matched and connected with the inner ring of the first rolling bearing 201;
the outer ring of the first rolling bearing 201 is connected with the shell 280 in a matching way; the connection mode has axial movement and radial fixed rotation;
the needle teeth 204 distributed in a conical shape of the precession needle gear 210 are matched and meshed in the internal teeth 2031 of the cover gear 203;
the spherical recess 103 is arranged at the axial center of the outer side of the outer ring 101 at one side of the transmission device, and the steel ball 207 is matched in the spherical recesses 2030 and 103 of the cover wheel 203 and the outer ring 101 of the transmission device;
one side of the input shaft 206 is connected with the inner ring 120 of the transmission device 1 in a matching way, and the other side of the input shaft 206 is fixedly connected with the inner ring of the second rolling bearing 202;
the outer ring of the second rolling bearing 202 is fixedly connected with the shell 280;
the housing 280 is a half gourd-shaped shell, a large-diameter inner chamber of the housing is connected with the first rolling bearing 201 in a matching manner, and a small-diameter inner chamber of the housing is connected with the second rolling bearing 202 in a matching manner, namely, the first and second rolling bearings, the cover wheel, the precession pin gear, the transmission device and the input shaft are wrapped by the two half gourd-shaped housings 280 and are radially connected with the housings by bolts (not shown); an elastic element 2011 is arranged between the outer edge 284 of the large-diameter inner chamber of the shell and the axial side end of the outer ring of the first rolling bearing 201; the elastic element 2011 is embedded in the groove 2022 of one of the two sides; the outer edge 285 of the small-diameter inner chamber of the shell 280 wraps the axial side end of the outer ring of the second rolling bearing 202; the first rolling bearing and the second rolling bearing are formed into a back-to-back mode of a bearing of a tapered roller;
the input shaft 206 drives the inner ring 120 of the transmission device 1 to rotate, the precession needle gear 210 on the outer ring 100 of the transmission device 1 is driven to revolve (precession) and rotate, the needle teeth 204 of the precession needle gear are in oblique cross meshing with the internal teeth 2031 on the cover wheel 203, the teeth in oblique cross meshing of the two are in progressive contact, the precession needle gear 210 rotates while revolving, and the rotation drives the output shaft 2032 of the cover wheel 203 to perform deceleration movement;
in the operation of the stable transmission device 1, the opposite slope type annular transmission element is a circular rolling transmission motion on the gear rings in the axial sides of the inner ring and the outer ring of the small gear set, the inner ring is driven to rotate, the small gear set drives the outer ring to revolve (precession) by taking the spherical center as a point by 360 degrees, a steel ball is arranged between the spherical concave part on one side of the outer ring and the spherical concave part of the cover wheel, the outer ring can move on the steel ball in the same precession manner, the steel ball is lifted to a supporting point and separates the outer ring and the cover wheel to form a relative precession angle in one rotation of the slope type annular transmission element in the device, one point of the spherical center and one point of the cone angle of the steel ball are formed, the precession needle gear connected with the outer ring in the motion revolves by two points to form a revolving moment, according to the angle setting of the slope type annular transmission element, the revolution needle gear revolves for a plurality of circles by a plurality of needle teeth, and the inner teeth of the precession needle gear in conical distribution in the revolution are crossed with the oblique angle vertical to the cover wheel to force the cover wheel to rotate at a low speed; here, the precession pin gear movement forces the cover gear to move axially outward, and the elastic element 2011 on the first rolling bearing has a moment to make the internal teeth of the cover gear and the pin teeth of the precession pin gear always keep meshed.
The setting ratio of the internal teeth 2031 and the needle teeth 204 can form at least two teeth of at least one party, and form teeth with the tooth difference of 1-9 times to 20 times, and the multiples of the internal teeth and the teeth of the needle teeth can be interchanged, and the angle of the slope type annular transmission element relative to the stable type transmission device is small, when the first teeth of the needle teeth and the first teeth of the internal teeth are in corresponding positions, when the inner ring rotates for one circle, the needle teeth are advanced (rotated) for several teeth to be meshed with the first teeth of the internal teeth, compared with the slope, the angle is large, and the teeth advanced (rotated) of the needle teeth are fewer. When the cover wheel is used as a cycloid speed increaser, the output shaft is converted into an input shaft to rotate at a low speed, the internal teeth of the cover wheel rotating at the low speed drive the needle teeth of the precession needle gear to do precession motion, and the output shaft connected with the inner ring rotates at an increased speed to output. In another embodiment, the precession pin gear is provided with a cylindrical shape corresponding to the cover wheel, or the precession pin gear is provided with a cone-shaped body corresponding to the inner periphery of the cover wheel and provided with an outward conical inner tooth.
The assembly mode is assembled from inside to outside in sequence.
Third embodiment
Fig. 27 and 28 show a third embodiment of a combined bearing and/or stable transmission 3, which shows sloping circumferential rolling elements as asymmetrical spherical rollers 351,352, the combination of asymmetrical spherical rollers being configured such that the contact rolling surfaces on both sides form an angle, the slope angle ranging from more than 0 ° to 10 °, preferably from more than 0 ° to 6 °. The drive rolling surfaces 381,382, 399 in the axial sides of the inner and outer races 380, 301,302 of the apparatus are configured in the shape of asymmetric spherical rollers and the radii of the drive rolling surfaces 381,382, 399 are slightly larger than the radii of the asymmetric spherical rollers 351, 352. The first and second stepped spherical raceways 905,906, ball rows 907,908 and outer spherical raceway 909 of the combination bearing and/or stabilizer transmission 3 have the same features as those of the first embodiment. The axis of the inner ring 380 and the axis of the outer ring 300 are opposite to form an angle o, the inner ring is driven to rotate, the outer ring automatically rotates around the axis of the outer ring, and meanwhile, the axis of the outer ring revolves around the axis of the inner ring. The function, principle and assembly are the same as in the first embodiment, and the dynamics of this stabilized precession motion can be used in the relevant mechanical field.
Fourth embodiment
Fig. 29 to 39 show a fourth embodiment of a cycloidal reducer/cycloidal speed increaser 400 using a combination bearing and/or a stationary transmission 1, 3. The illustrated cycloidal reducer/cycloidal speed increaser 400 includes: a precession cycloidal gear 401, a pinwheel 402, first and second rolling bearings 405,406, a driven wheel 404, an input shaft 407, and a housing 480;
the precession cycloidal gear 401 is arranged in a conical cover shape, the bottom of the cover is provided with a plurality of through round parts 4012, the periphery of the precession cycloidal gear is provided with conical external teeth 4011, the inner periphery of the precession cycloidal gear is sleeved on the outer ring at one side of the transmission device 3 and fixedly connected, and a pin is inserted into matching grooves of the two;
a needle groove 4021 is formed in one side of the inner periphery of the needle wheel 402, the needle teeth 403 are movably matched in the needle groove 4021, an annular flange 4022 is formed in the other side of the inner periphery of the needle wheel, and the outer periphery of the annular flange 4022 is fixedly connected with the housing 480;
the inner periphery of the annular flange 4022 of the pinwheel 402 is fixedly connected with the outer ring of the first rolling bearing 405;
an output shaft 4042 is arranged on one side of the driven wheel 404, a plurality of circular convex parts 4041 are arranged on the other side of the driven wheel, and the outer periphery 4043 of the driven wheel is connected with the inner ring of the first rolling bearing 405 in a matching manner;
the plurality of circular convex portions 4041 of the driven wheel 404 are fitted in the plurality of through-circle portions 4012 of the precession cycloidal gear 401, and the diameter of the through-circle portion of the precession cycloidal gear is larger than that of the circular convex portions of the driven wheel; the contact surface of the further circular convex portion 4041 in cooperation with the through circular portion 4012 is configured as a precession rotation inclination angle of the transmission 3;
one side of the input shaft 407 is connected with an inner ring 380 of the transmission device 3 in a matching manner, the other side of the input shaft 407 is connected with an inner ring of a second rolling bearing 406 in a matching manner, and an outer ring of the second rolling bearing 406 is fixedly connected with a shell 480;
the housing 480 is a half gourd-shaped shell, the large-diameter inner chamber of the housing 480 is connected with the outer diameter of the pinwheel 402 in a matching manner, and the small-diameter inner chamber of the housing is connected with the second rolling bearing 406 in a matching manner, that is, the pinwheel 402 and the second rolling bearing 406 are wrapped by the two half gourd-shaped housings, and the housing 480 is radially connected by bolts (not shown);
the input shaft 407 drives the inner ring 380 of the transmission device 3 to rotate, the precession cycloidal gear 401 on the outer ring 300 of the transmission device is driven to precession (revolve), the conical external teeth 4011 of the precession cycloidal gear are in oblique cross meshing with the movably connected needle teeth 403 on the fixed needle wheel 402, the teeth in oblique cross meshing of the conical external teeth 4011 and the fixed needle wheel are in progressive contact, the precession of the precession cycloidal gear 401 forms low-speed rotation of external teeth 4011 revolution torque meshing with the needle teeth 403, so that the driven wheel 404 is driven to rotate, and the driven wheel 404 rotates at a speed reduction under the difference of the number of teeth and in the low-speed rotation. The tooth difference is 1-20 teeth, and the tooth difference can be converted. When the output shaft and the input shaft are interchanged, a cycloid speed increaser is formed. Under the characteristics, in another design, the precession cycloidal gear is provided with a cylinder corresponding to the needle wheel, or the precession cycloidal gear is provided with a conical cover corresponding to one side of the inner circumference of the needle wheel and provided with an outward conical needle groove, the needle teeth are movably matched in the needle groove, and the other side of the inner circumference is provided with an annular flange.
The illustrated teeth 403 may be made of teflon, which provides lubrication.
Fifth embodiment
Fig. 40-45 and 45 a-45 f show a cage and/or a planetary tray carrier 500 of a combined bearing and/or transmission provided by a fifth embodiment;
an axial cage and/or planetary pallet 500 for a stable or passive or active transmission, according to which two side transmission rolling surfaces in the axial direction of the split outer ring and two side transmission rolling surfaces in the axial direction of the inner ring are configured to arrange the transmission rolling surfaces of the pair of transmission elements; the pair of transmission elements in the axial direction are configured by the axial cage to engage the ball rows to facilitate movement of the transmission rolling surfaces in contact in the axial direction of the transmission and are guided by the cage to maintain contact between the transmission rolling surfaces in the axial direction;
the section of the axial annular retainer 500 forms a T-shaped inner circumference side 520 and an outer circumference side 510, the upper part of one T-shaped rotation circle is the inner circumference side 520, the lower part of the T-shaped rotation circle is the outer circumference side 510, the annular section of the inner circumference side 520 forms a corresponding slope shape and/or a parallel shape, a certain distance is reserved between the edge of the inner end surface of the shaft hole extending to the axial direction of the outer ring at one side of the T-shaped upper part and the edge of the axial side end surface extending to the inner ring at the other side of the T-shaped upper part, rubber sealing rings 530,531 are sleeved on the annular outer diameters at the two axial sides of the T-shaped upper part and abut against the axial parts of the inner ring and the outer ring, and window type pockets 511 uniformly distributed around the periphery are formed on the outer circumference side 510 of the T-shaped lower part;
the axial cage window pocket 511 is configured in the shape of a transmission element 550,558, two sides of the axial line of the window pocket 511 radiating relative to the central rotating shaft of the cage are provided with two axially opposite or axially same-direction grooves 518,519 matched with a connecting mandrel 599, the axial line of the two axially opposite or axially same-direction grooves 518,519 is configured to be conical radiation or vertically radiated relative to the central rotating shaft of the cage, the mandrel 599 is configured that two ends of a round rod form concave-convex portions 590 which are correspondingly matched in the two-side grooves 518,519 on the window pocket; the mandrel 599 passes through flange-shaped elements (not shown, shown in the following embodiments) which are matched with the two ends of the shaft holes of the transmission elements 550 and 558, the elastic element 570 penetrates through the mandrel 599 and is arranged at the large-diameter end side of at least one of the transmission elements 550 and 558, one side of the elastic element 570 is abutted against the radial end line part or end part of the window-type pocket 511, and the other side of the elastic element 570 is abutted against the flange-shaped element end face; in the region of the window pocket 511 of the retainer 500, a two-part snap-in device is provided, which is formed by a front face and a front face, and in which two-end flange-like elements on the transmission elements 550,558 abut against the radial front face or front face of the window pocket and the spring element 570 in order to hold the transmission elements 550,558 in the pocket 511, and which allows insertion of the transmission elements into the pocket by elastic deformation in the region of a front face of the spring element and a front face or front face of the window pocket; the axes of rotation of the plurality of transmission elements 550,558 are arranged radially around a cone or radially perpendicular to the central axis of rotation of the cage; on the one hand, the circumferential displacement of the transmission elements 550,558 is controlled by a radial force of the spring element 570 on the cage 500 in cooperation with a force of the axial spring element, and on the other hand, the conical transmission element, which allows for tolerances during the production process, is held in contact with the transmission running surface in the axial side, in the course of the axial and radial forces, when the end face of the flange on the side of the small-diameter end of the conical transmission element does not come into contact with a terminal portion or end of the pocket. The features and design considerations described in the first embodiment can be taken into account here, the ring diameter on the inner peripheral side of the cage being formed at a distance from the inner diameter of the shaft bore of the outer ring, depending on the data values used for the different bearings and/or devices.
Sixth embodiment
Fig. 46 to 49 show a sixth embodiment of a planetary reducer/planetary speed increaser 7 using a combination bearing and/or a stationary transmission. The planetary reducer or speed increaser with opposed transmission elements, the planetary reducer 7 is tightly combined on the housing by a split internal toothed ring sleeve 700 (a ring gear or an axial raceway surface can be formed in the axial side of the split outer ring) in one axial direction, the internal toothed ring sleeve 700 (the split outer ring) has a first planetary element set 741 (axial transmission element) which is driven by external power and is combined by a plurality of elements in an equal way on the tray 731, a second planetary element set 742 (axial transmission element) which is combined by a plurality of elements in an equal way on the output side on the other axial side on the tray 732, a central sun driven wheel 720 (a ring gear or an axial raceway surface can be formed in the axial side of the inner ring) is between the output side and the input side, and the tray 731,732 of the planetary transmission elements 741,742 is supported by the input shaft 751 and the output shaft 752, the floating internal teeth 700 and the sun driven wheel 720 in the meantime; when the input side power drives the first planetary gear 741 connected to the input shaft 751 of the tray 731, the sun driven wheel 720 is driven to rotate, so as to drive the output side second planetary gear 742 to rotate and drive the output shaft 752 connected to the tray 732 to output power, and the opposite planetary gear 741,742 revolves along the central rotation axis at the axial diameter ratio of each group of elements (axial distance of one element relative to axial distance of the other element or tooth difference of the small gear set) and following the track of the inner gear sleeve 700. The planetary transmission element group is arranged as follows: rolling elements, pinion sets, ramped circumferential rolling elements (drive elements), ramped ring gear sets (drive elements). The rolling bodies in the axial side are in rolling friction transmission, the pinion gear set in the axial side is in gear friction transmission, and the central sun driven wheel performs balanced rotary motion; the slope type circumferential rolling elements in the axial side are in rolling friction transmission, the slope type annular gear set (a right-angle gear set of a ring gear and a pinion, a common or universal ring gear, the pitch diameter and the tooth number of the ring gear are meshed with the pinions with various tooth numbers, namely, a 6, 7, 8 and 9/39 ring gear is provided, the characteristics are the same as those of the first embodiment) in the axial side is in gear friction transmission, and the central sun driven wheel is in two compound motions of precession motion and rotation motion. The planetary reduction gear 7 is formed as a planetary gear set with the input side and the output side exchanged.
In an advantageous embodiment of the planetary gear reducer, the reducer or the speed increaser using the combination bearing and/or the transmission comprises the combination bearing, the stable transmission, the passive transmission and the axial retainer;
two axially opposite small gear sets (planet gears) on two sides of the sphere center of the combined bearing and/or the bearing of the transmission device are matched with a transmission rolling surface in the axial direction to run; the transmission rolling surface is constructed into an annular plane gear;
the tooth number of the annular plane gear teeth formed by the transmission rolling surfaces of the inner ring and the outer ring on one side of the sphere center in the axial direction is matched with the tooth number of the annular plane gear teeth formed by the transmission rolling surfaces of the inner ring and the outer ring on the other side of the sphere center of the pinion set to be matched with the pinion set to form tooth difference of the two sides;
the small gear set is formed by uniformly distributing axial retainers (planet carriers), the input shaft is tightly matched and connected with the inner diameter of the inner peripheral side of the axial retainer on one side, and the output shaft is tightly matched and connected with the inner diameter of the inner peripheral side of the axial retainer on the other side;
the outer ring at one side of the split outer ring (inner gear ring) is tightly matched and connected with the shell;
the ring-shaped face gear on the outer ring is composed of a flat ring (shown in fig. 3 to 12 of the first embodiment) and the opposing faces of the teeth of the flat ring are provided with a plurality of convex portions that fit a plurality of concave portions on the axial side of the outer ring;
the input shaft directly gives a rotary input to one of the pair of axial retainers to drive the pinion set to rotate so that the pinion set rolls along the annular plane gear of the outer ring at the static side to drive a sun gear (inner ring) to implement first-stage speed change, and simultaneously the pinion set at the other side rolls along the annular plane gear of the outer ring at the static side to drive the axial retainers to implement second-stage speed change of an output shaft connected with the retainers. The difference in teeth formed by the sets of pinions in the pair is such as to effect a variation in at least one kinematic parameter between drive and output.
The reduction or speed increaser is designed as a passive transmission in such a way that the pinion and/or the rolling bodies are arranged opposite one another in a conical arrangement (not shown) with the features of the passive transmission which are arranged axially and with the transmission elements, which are referred to here in relation to the transmission movement, the central concept of the combination with the other features of the application being clear and not described.
The matching of the ring plane gear and the small gear set in the axial side is a right-angle gear set of the ring gear and the small gear, the tooth profile of the small gear forms a bevel gear and an asymmetric spherical gear, and the tooth profile of the ring gear is configured to the tooth profile of the small gear. In another arrangement, the cooperation of the annular face gear in the axial side with the pinion gear set is a crown gear having a 90 degree shaft angle and a pinion gear as a spur gear.
It is further recognized that the opposite transmission elements or rolling bodies in the axial sides of the planetary reducer/planetary speed increaser 7 of the embodiment can be formed as: the parallel and/or symmetrical fitting opposition of the axes of rotation of the cylindrical rollers, spherical rollers, tapered rollers (tapered, asymmetrical spherical rollers) themselves, the drive raceway surfaces in the ball and axial sides are configured as a form fit of the rolling bodies.
Seventh embodiment
FIGS. 50-54 illustrate a fifth embodiment of a bicycle 8 utilizing a stationary transmission and a passive transmission that incorporates bearings and/or transmissions;
according to the stable type 1 and the passive type transmission device (not shown), two feet of a user step on the outer ring of the transmission device 800 movably connected with a thrust bearing 810 of a pedal 820 to do rotary and precessional motion to drive the inner ring to rotate, a bevel gear 840 fixedly connected with an output shaft 890 connected with the inner ring drives bevel gears 850 and 851 fixedly connected with wheels 860,861 to drive the wheels 860,861 to run;
the power device of the bicycle 8 shown in fig. 50-54 is constructed by connecting a pedal 820, a thrust bearing 810, a transmission device 800, an output shaft 890 and a downward bevel gear 840 vertically from top to bottom, and arranging a positioner 830 on the output shaft 890 between the transmission device 800 and the bevel gear 840; the structure of the wheels 860,861 is shown, the left and right double-row wheels 860,861 are connected by a central shaft, the two ends of the central shaft are connected with a surrounding rod 870 and a connecting rod 871, the inner side of each wheel of the double-row wheels 860,861 is connected with a first bevel gear 850 and a second bevel gear 851, a bevel gear 840 is arranged between the first bevel gear 850 and the second bevel gear 851, and one side of the first bevel gear 850 and one side of the second bevel gear 851 are in left-right moving positioning contact meshing with the bevel gear 840 through a positioner 830; the positioner 830 comprises an adjusting screw 831, a sleeve 832 and a rolling bearing 833 combination, wherein the rolling bearing 833 is movably connected in an oval sleeve 832 (shown in figure 54), the inner ring of the rolling bearing is connected with an output shaft 890, the outer ring of the rolling bearing is connected with the sleeve, two ends of the sleeve are connected with two sides of a surrounding rod 870, the left and right adjusting screw 831 penetrates through a through hole of the surrounding rod and is matched with the through hole of the sleeve to squeeze the adjusting rolling bearing left and right relatively, so that a bevel gear 840 is meshed with a first bevel gear 850 and a second bevel gear 851 on one side, the lower part of a front fork 881 is movably connected with a connecting rod 871, the upper part of the front fork 881 is movably connected with the upper part of the surrounding rod 870, the lower end of the front fork 881 is provided with a front wheel 862, and the upper end of the front fork 881 is provided with a steering wheel 880. The user adjusts the wheel driving on the side to advance according to the motion swinging habit of the user.
The stable transmission device 1 is adopted in the design, a user steps on the pedal by one foot, the other foot pushes the driving wheel to rotate off the ground, meanwhile, the lifting foot makes a swinging motion on the pedal, the bicycle runs, when the user stops moving, the inertia of the wheel motion can drive the stable transmission device to make a procession motion all the time, and the stable transmission is mutual transmission; in another design, a passive transmission device (not shown) is adopted, and after the user starts the bicycle to run firstly and then swings to drive the wheels to rotate, the user stops moving, the outer ring of the passive transmission device stops precession, the inner ring and the outer ring form pure rolling under the action of inertia, the device is converted into supporting rotary motion, the user continues swinging precession motion (external force), the outer ring of the passive transmission device precesses to drive the inner ring to form torque rotation, and the device is converted into driving motion of the wheels.
Eighth embodiment
Fig. 55 to 59 show an eighth embodiment of the opposed type speed reducer/opposed type speed increaser 6 using a combination bearing and/or transmission.
A further combination bearing and/or transmission is described having features common to the first to eighth embodiments of the present application throughout the drawings, and the features of the outer race first stepped spherical raceway 905, second stepped spherical raceway 906, ball rows 907,908, inner race outer spherical raceway 909, and the like in the combination bearing and/or transmission shown are labeled the same, as will be repeated herein.
The illustrated combination bearing and/or the passive transmission of one of them, yet another combination design, has an opposed mating configuration with at least two inner central sun gears 620 forming an axially split, i.e. one set of transmission elements 630 is added between the two sun gears 620, the outer spherical raceway surfaces 909a,909b of each set of sun gears 620 in the radial direction forming a rolling and sliding movement with the ball rows 907,908 and the inner spherical raceways 905,906 of the split inner ring gear 600, the additional pair of transmission elements 680 fitting on both outer sides of the opposing split sun gear 620, the split inner ring gear 600 that externally surrounds them, having a common rotational centerline through-hole, the input side AX fitting closely the inner diameter of one sun gear, the output side AF fitting closely the inner diameter of the other sun gear, the split inner ring gear 600 being axially connected by screws 91 making them integral, forming a reduction and/or transmission gear ring in the split sun gear 620; the movement of the auxiliary pair of gear elements 680 in the axial side is a rolling movement of the rolling elements and the bearings and/or the gear running surfaces of the split inner toothed ring sleeve 600 of the device 6 and the axial side of the sun wheel 620 are configured in the shape of rolling elements, the two sides of the middle of the split sun wheel 620 form annular gears and/or gear running surfaces, the central set of gear elements 630 are formed between the split sun wheel 620 as small gear sets and/or rolling elements, the central small gear sets and/or rolling elements are distributed as common by the carrier 631, the central small gear sets and/or rolling elements form a concentric and integral configuration of the size of the steps of each gear element, i.e. the stepped gear element 632 forms a large diameter end 6320 and a small diameter end 6321, each gear of the small gear sets forms a different number of teeth step gear (not shown) between the large diameter end and the small diameter end, the annular step gear(s) distributed annularly by the axial cage and/or planetary carrier 631 is distributed annularly on the other side between the split sun wheel 620, i.e. the annular step gear on the side the annular step gear of the annular gear 621 of which is in the axial direction of the sun wheel is in contact with the split sun wheel 622, the small diameter end of the annular gear of the split sun wheel 621; a clamping ring 690 is further provided between the split type inner toothed ring sleeves 600 and the radial outer diameter of the tray 631 of the central transmission element group 630, the clamping ring 690 is formed as two semicircular rings or movable connectors facing each other in the circumferential direction, the semicircular rings of the clamping ring have a T-shaped cross section, the upper portion of the T-shape is an outer circumferential side, the lower portion of the T-shape is an inner circumferential side, the diameter of the outer circumferential side is larger than the outer diameter of the inner toothed ring sleeves 600, the inner periphery side is positioned between the two adjacent parts of the inner tooth ring sleeve and is not contacted, a plurality of screw through holes 6901 are arranged on the inner periphery side and are larger than screw holes 9 on the inner tooth ring sleeve, the screw through holes are correspondingly communicated with the screw through holes, the inner diameter clamping surface 6902 on the inner periphery side is contacted and fastened with the outer diameter surface of the tray 631, an elastic element 695 is arranged between the inner diameter surface 6903 on the outer periphery side and the outer diameter of the inner tooth ring sleeve to form two semicircular rings, and the semicircular rings form wavy elastic steel sheets; the two sides of the outer diameter of the outer circumference side form a slope 6904, which is pressed against the slope surface 6904 of the clamping ring 690 by the axial movement of a sleeve (not shown) of an external force, to force the elastic steel sheet 695 to deform, so that the inner diameter clamping surface 6902 of the clamping ring 690 is fixed in contact with the outer diameter surface of the tray 631; here one force of the clamping ring causes each element of said central driving element group 630 to spin on the spindle 640; on the other hand, without external force, the elastic steel sheets 695 make the holding ring 690 leave the outer diameter surface of the tray 631 radially, the central driving element group 630 revolves, the input side rotates synchronously with the output side, and the central driving element group 630 revolves and rotates when the output side has partial external force or is fixed; as shown in fig. 58, the orientation of the concave portion 6311,6312 (fig. 59) of the holder 631, which is provided and assembled in accordance with the orientation of the large diameter end 6320 and the small diameter end 6321 of the step gear element 632, is coupled and combined with the concave and convex portions 641, 642 of the core shaft 640, and fig. 58 shows the case where the large diameter end 6320 of the step gear element 632 is distributed on the outer peripheral side, the outer peripheral concave portion 6311 of the holder 631 is distributed in the direction of the one side sun gear 621 on the left side, the small diameter end 6321 is distributed on the inner peripheral side, and the inner peripheral concave portion 6312 of the holder 631 is distributed in the direction of the other side sun gear 622 on the right side; the center of the end faces of the two sides of the stepped transmission element 632 shown in fig. 58 is provided with a concave part communicated with the mandrel hole, the concave parts of the two sides are larger than the diameter of the mandrel hole, the concave parts of the two sides are embedded into the flange plate 650, after the mandrel 640 of the flange plate is inserted into the shaft hole of the transmission element 632, the spring 660 is sleeved on the two ends of the mandrel 640, and the stepped transmission element 632 is connected with the inner concave part 6312 and the outer concave part 6311 in the window hole 6310 (fig. 59) of the retainer 631; the split sun gear 620 shown here has drive raceway surfaces 625,626 on one side of the sun gear 621 on both sides of the axially intermediate drive raceway surfaces 625,626 in the form of annular flat surfaces contacting large diameter ends 6320 of the drive elements 632, and drive raceway surfaces 626 on the other side of the sun gear 622 in the form of annular stepped surfaces defining concave portions 628 and convex portions, with the drive raceway surfaces having annular inner peripheral convex portions 626 contacting small diameter ends 6321 of the drive elements 632, and a collar made of a polymer material may be provided on a radial end face 6280 connecting the annular stepped concave portions 628 and the convex portions 626;
the assembly of the illustrated counter-type reduction gear/counter-type speed increaser 6 is basically assembled from inside to outside, and finally the screw holes 9 of the split internal toothed ring sleeve 600 are connected by screws (not shown), and the gap between the auxiliary pair of rolling elements 580 and the central transmission element 630 in the axial direction is in mating contact with elastic elements provided on the nuts of the screws on the internal toothed ring sleeve.
On the other hand, the tray (not shown) may be provided with an abutting portion extending radially to the split inner ring housing 600 without contact therebetween, and a screw 9 formed on the inner ring housing passes through a screw through hole formed on the tray to fix the tray in a rotational direction without rotation; the central sun-split opposing reduction and/or speed increaser 6 has a stepped gear 632 configured such that a transmission ratio of at least one order of magnitude is formed between the input side and the output side.
It is further recognized that the opposing transmission elements or rolling elements in the axial sides of the opposing reduction gear/opposing speed increaser 6 of the exemplary embodiment can be formed as: cylindrical rollers, spherical rollers, tapered rollers (tapered, asymmetrical spherical rollers) are arranged in parallel and/or symmetrical fitting opposition to the center axis of rotation of the rollers themselves, balls, and the drive raceway surfaces in the axial sides are configured as a positive fit for the rolling bodies.
Ninth embodiment
The following, not shown, may refer to the divisional application nos.: 202280002318.6, all of which are hereby incorporated by reference.
The passive transmission device is matched with at least one rolling body for transmission, the rolling bodies are oppositely matched at two sides of the inner ring and the outer ring in the axial direction, and the rolling bodies are uniformly distributed by the annular axial retainer;
the inner ring and the outer ring in the radial direction form spherical raceways which are overlapped relative to the centers of matched steps, namely, the spherical raceways of the inner ring and the outer ring are separated and overlapped to form two spherical raceways of at least one step;
the outer ring forms a split outer ring matched with at least one of the two in the axial direction, and the outer diameters of the two outer rings are different;
the two outer sides of the split outer ring in the axial direction are partially coated with a distance part to form transmission rolling surfaces in the axial direction of the inner ring and the outer ring which are matched with each other, namely, the transmission rolling surface of the inner ring on one axial side of the spherical center is a conical rolling surface of which the conical rolling surface is matched with the transmission rolling surface of the outer ring on the other axial side of the spherical center, and the annular axial transmission rolling surfaces of the inner ring and the outer ring are correspondingly matched with the conical transmission rolling surfaces; such that the rolling bodies are configured as rolling bodies of said transmission rolling surface;
the ball rows are in contact with the spherical raceway in a point manner, so that the ball rows are easy to roll and firstly bear at least one part of load, and the superposed spherical raceway surfaces of the inner ring and the outer ring are easy to be in sliding contact and bear the other part of load;
a plurality of bolt holes matched with at least one split outer ring are formed in the outer periphery of the outer side of the split outer ring in the axial direction, the two outer rings are oppositely connected through the bolts matched with at least one split outer ring, and the outer ring on one side of the split outer ring is in interference fit with the bearing box body;
the running clearance of the ball rows in the transmission device in the axial direction is matched and pre-tightened by a plurality of elastic elements matched on the plurality of bolts, and the running circumferential clearance of the transmission rolling bodies in the transmission device in the radial direction is automatically adjusted by matching a plurality of elastic elements matched on the retainer with the elastic elements on the plurality of bolts;
the transmission rolling body is constructed to relatively control at least one motion of precession motion and/or support revolution motion of the inner ring and the outer ring in the transmission rolling surface motion correspondingly in the operation of at least one of the combined sliding-rolling ratio and the flexibility freedom of the rolling motion of at least one pair of ball rows of the inner ring and the outer ring and the sliding motion of the coincident spherical roller paths of the inner ring and the outer ring under at least one external moment;
the conical transmission rolling surfaces on two sides of the spherical centers of the inner ring and the outer ring are matched with the transmission device of the annular axial transmission rolling surface to drive the inner ring to rotate, the outer ring carries out precession motion towards the other direction under the external moment, and/or the conical transmission rolling surfaces on two sides of the spherical centers of the inner ring and the outer ring are matched with the transmission device of the annular axial transmission rolling surface to drive the outer ring to rotate, the inner ring carries out precession motion towards the other direction under the external moment, and/or the outer ring or the inner ring of one party carries out precession motion to drive the inner ring or the outer ring of the other party to carry out rotary motion towards the opposite direction, and/or the outer ring or the inner ring of one party carries out rotary motion to drive the inner ring or the outer ring of the other party to carry out relative supporting rotary motion;
the conical arrangement of the conical surface of the drive rolling surface relative to the precessional motion achieves a drive ratio of the inner and outer races, the drive being configured such that a change in at least one motion parameter between drive and output is achieved;
the following explains the action and principle described by the tapered rollers in the axial side of the passive transmission (or bearing):
the pair of tapered rollers (tapered, asymmetric spherical rollers) are directed in one direction with their own rotational center axes.
When the tapered rollers in the left row and the right row can be opposite to each other and are not parallel in the bearing during installation (installation is not parallel and not shown), the rolling surfaces of the left row are controlled to be relatively parallel by the axial ring plane roller path of the first roller path of the inner ring, the central axis of the left row is relatively parallel to and does not coincide with the rotation axis of the inner ring, the central axis of the left row is not parallel to but intersects with the central axis of the outer ring during rolling, the central axis of the left row moves circumferentially around the central axis of the inner ring, the rolling surfaces of the right row are controlled to be relatively parallel to and do not coincide with the central axis of the second outer ring during rolling, the central axis of the right row is not parallel to but intersects with the rotation axis of the inner ring during rolling, and the central axis of the right row moves circumferentially around the central axis of the outer ring. Between the tangent conical surface raceway and the planar raceway of each row of conical rollers, the rotation axes of the inner ring and the outer ring are relatively inclined, namely the planar raceway of the inner ring is not parallel to the planar raceway of the outer ring, the left and right rows of conical rollers roll relatively in an inclined manner on the conical surface raceway surface by an inertia space track, and when the inner ring of the bearing rotates relative to the outer ring, the left and right rows of conical rollers which are relatively inclined rotate at high speed to drive the outer ring to do rotary swing motion and the outer ring can rotate towards the opposite direction, namely what is commonly called precession motion. In the process, the outer ring of the bearing moves in a precession mode, the inner ring rotates at a high speed, if an external force is applied, the included angle of the central axes of the inner ring and the outer ring is driven to change at any time, the angle of the relative central axis is changed at any time, but the included angle of the central axis is in a control range, the outer diameter of the ring part (not shown) of the inner periphery of the retainer (the outer part of the inner peripheral side of the upper part of the T-shaped section of the retainer) forms a distance with the through hole of the outer ring, and the precession angle of the bearing is controlled. If the inner ring of the bearing continuously rotates at high speed and no external force exists, the bearing returns to the pure rolling motion, the pair of tapered rollers returns to the spatial parallel, and the rotating direction of the outer ring relative to the inner ring stops.
If the driving mode is changed, the outer ring is driven to precess when the two rows of tapered rollers are not parallel, and the inner ring is driven to rotate in the opposite direction, and vice versa, the tapered roller driving device can be applied to general-purpose machines.
The transmission rolling bodies or transmission elements can be designed into tapered rollers, asymmetric spherical rollers and balls, and the transmission rolling surface motion of the transmission elements on the axial side is contact friction motion; in a further embodiment, the transmission element is formed as a pinion set: the transmission device comprises a conical gear, an asymmetric spherical gear and a transmission rolling surface matched with a small gear set to form orbital transmission surfaces with different tooth profiles, wherein the orbital surface motion of the transmission element small gear set at the axial side is tooth-tooth contact friction motion, the tooth-tooth contact friction motion can only be used as supporting rotation motion and transmission motion in the tooth-tooth matching motion, and point contact rolling, surface contact sliding motion and tooth contact rolling transmission motion of a ball row are formed inside the transmission device.
Tenth embodiment
Further applications of these machines can be made with the above combination bearing and/or transmission including an internal combustion engine or a fluid machine (cited in the summary of the invention) or a wind power plant, by reference to the functional references described in the seventh embodiment, which are not illustrated.
List of reference numerals
Claims (14)
1. A stable transmission device (1, 3, 7 a) mating at least one of ramp type ring transmission elements (141, 142, 351,352, 741, 742), the ramp type ring transmission elements (141, 142, 351,352, 741, 742) are correspondingly fitted on both sides of the axial direction of the inner and outer rings (120,100, 380,300, 720,700), a plurality of transmission elements of the ramp type ring transmission elements (141, 142, 351,352, 741, 742) are evenly distributed by the annular axial cage, each transmission element of the ramp type ring transmission elements forms an angle in a ramp manner around the ring shape, that is, the side surface of a combination of a plurality of transmission elements of a circular array passes through the central axis and is diagonally split into a pair;
the inner and outer rings in the radial direction form spherical raceways (909, 905, 906) that coincide with the centers of the mating steps, i.e., the spherical raceways (909, 905, 906) of the inner and outer rings are separated and coincide to form at least two spherical raceways of at least one step;
the outer ring (100, 300, 700) in the axial direction is formed as a split outer ring (101, 102, 301,302, 701, 702) mating at least one of them, and the outer diameters of the two outer rings are different in size;
the stepped spherical raceways (909, 905) of the inner ring and the outer ring form a pair of axially distributed ball rows (907, 908) which are matched with at least one of the inner ring and the outer ring, the ball rows are held at two axial sides of a sphere center by a ball ring holder, the diameter of each ball of each pair of the ball rows is slightly larger than a data value than the distance from the inner ring to the outer ring corresponding to the position of the ball, the ball rows are formed to be in point contact with the spherical raceways and easily roll to firstly bear at least one part of load, and the surfaces of the overlapped spherical raceways (909, 906) of the inner ring and the outer ring are easily in sliding contact to bear the other part of load;
the two outer sides of the split outer ring in the axial direction are partially coated with a distance to form transmission rolling surfaces (121, 122, 133,134, 381,382, 399, 722,707) in the matched axial sides of the inner ring and the outer ring and the corresponding of the overlapped and separated spherical raceways of the inner ring and the outer ring, so that the slope type annular transmission element is constructed into the transmission element of the transmission rolling surfaces;
a plurality of bolt holes (9) matched with at least one split outer ring are formed in the outer periphery of the outer side of the split outer ring in the axial direction, the two outer rings are oppositely connected through the bolts (91) matched with at least one split outer ring, and the outer ring on one side of the split outer ring is in interference fit with the bearing box body;
the running clearance of the ball rows in the transmission device in the axial direction is matched and pre-stressed by a plurality of elastic elements matched on the plurality of bolts, and the running circumferential clearance of the slope type annular transmission element in the transmission device in the radial direction is automatically adjusted by a plurality of elastic elements (570, 660) matched on the retainer and the elastic elements on the plurality of bolts;
the slope type annular transmission element is constructed to control the precession motion of the inner ring and the outer ring in the transmission rolling surface motion correspondingly in the combined rolling ratio and flexibility of the rolling motion of at least one pair of ball rows of the inner ring and the outer ring and the sliding motion of the coincident spherical raceways of the inner ring and the outer ring;
the transmission device with the slope type annular transmission element drives the inner ring to rotate so as to drive the outer ring to perform precession motion towards the other direction, and/or the transmission device with the slope type annular transmission element drives the outer ring to rotate so as to drive the inner ring to perform precession motion towards the other direction, and/or the outer ring or the inner ring of one party performs precession motion so as to drive the inner ring or the outer ring of the other party to perform rotational motion towards the opposite direction;
the ramp angle of the ramped annular drive element is sized to achieve a drive ratio of the inner race to the outer race, the transmission being configured such that a change in at least one parameter of motion is achieved between drive and output.
2. An axial cage and/or planetary carrier (500) comprising a stationary transmission according to claim 1, characterized in that: both side transmission rolling surfaces in the axial direction of the split outer ring and both side transmission rolling surfaces in the axial direction of the inner ring are configured to configure the transmission rolling surfaces of the pair of transmission elements; the pair of transmission elements in the axial direction are configured by the axial cage to cooperate with the ball rows to facilitate movement of the transmission rolling surfaces in contact in the axial direction of the transmission and to be guided by the cage to maintain contact between the transmission rolling surfaces in the axial direction;
the section of the annular retainer (500) forms a T-shaped inner circumference side (520) and an outer circumference side (510), the upper part of one circle of T-shaped rotation is the inner circumference side (520), the lower part of the one circle of T-shaped rotation is the outer circumference side (510), two sides of the annular section of the inner circumference side form corresponding slope shapes and/or parallel shapes, a certain distance is reserved between the edge of the end face of the axial inner end face, which extends to the outer ring, of one side of the upper part of T-shaped, and a certain distance is reserved between the edge of the end face of the axial end face, which extends to the inner ring, of the other side of the upper part of T-shaped, the annular outer diameters of two axial sides of the upper part of T-shaped are both sleeved with rubber sealing rings (530, 531) which are abutted to the axial parts of the inner ring and the outer ring, and the outer circumference of the lower part of T-shaped forms window type pockets (511) which are uniformly distributed around the ring;
the window pocket (511) of the axial retainer (500) is configured into the shape of a transmission element (550,558), two side grooves (518,519) which are opposite to each other in the axial direction or are in the same direction in the axial direction are arranged on two sides of the axis of the window pocket which is radiated relative to the central rotating shaft of the retainer, the two side grooves (518,519) which are opposite to each other in the axial direction or are in the same direction in the axial direction are matched and connected with a mandrel (599), the axis of the two side grooves (518,519) which are opposite to each other in the axial direction or are in the same direction in the axial direction is configured into conical radiation or vertical radiation relative to the central rotating shaft of the retainer, and the mandrel (599) is configured into a round rod with concave-convex part (590) which is correspondingly matched in the two side grooves (518,519) on the window pocket; the mandrel penetrates through flange-shaped elements matched with two ends of a shaft hole of the transmission element, the elastic element (570) penetrates through the mandrel (599) and is configured on the large-diameter end side of at least one of the transmission elements, one side of the elastic element (570) is abutted against the radial end line part or end part of the window type pocket, and the other side of the elastic element is abutted against the flange-shaped element end face; in the window pocket area of the retainer, a two-part snap-in device is provided, which is formed by a terminal or an end and an end face, and the two-end flange disk-shaped element on the transmission element (550,558) abuts against the radial terminal or the end of the window pocket and the elastic element for holding the transmission element in the pocket, and which allows the insertion of the transmission element into the pocket by elastic deformation in one face of the elastic element and in the area of the terminal or the end of the window pocket; the rotation axes of the plurality of transmission elements are arranged around a conical radiation or are arranged perpendicular to the central rotation axis of the holder in a radiation manner; the transmission element (550,558) is circumferentially displaced under the control of a force, on the one hand, of the radial elastic element on the cage (570) which cooperates with a force of the axial elastic element.
3. A stabilized transmission (3) comprising a stabilized transmission, an axial cage, paired with at least one ramped annular transmission element according to claims 1 and 2, characterized in that: the drive elements of the ramped ring drive elements are run by asymmetric spherical rollers (351, 352) fitted in drive running surfaces (381, 382, 399) on the axial sides of the inner and outer races (380,300) and configured as the raceway surfaces of the asymmetric spherical rollers.
4. A stabilized transmission (1) comprising a stabilized transmission, an axial cage, paired with at least one ramped annular transmission element according to claims 1 and 2, characterized in that: the transmission elements of the ramp ring transmission element are operated by a pinion gear set (141, 142) in a transmission rolling surface (121, 122, 133, 134) on the axial side of the inner and outer rings (120,100), and the transmission rolling surface is configured as a gear-tooth ring plane gear (121, 122, 133, 134); the ring-shaped face gears on the outer ring axial side are composed of independent flat rings (131, 132), and the both-side ring-shaped face gears (121, 122, 133, 134) of the split outer ring are formed by providing a plurality of protrusions (112) on the opposing faces of the ring-shaped face gears (121, 122, 133, 134) on the flat rings (131, 132) to be fitted into a plurality of recesses (111) on the outer ring axial side.
5. A stationary transmission, axial cage and/or planetary carrier as claimed in any one of claims 1 to 4, characterized in that: the ramp angle of the ramped annular drive element ranges from greater than 0 ° to 10 °, preferably from greater than 0 ° to 6 °.
6. The passive transmission device matched with at least one rolling body for transmission comprises the axial retainer and/or the planetary tray according to claim 2, wherein the rolling bodies are oppositely matched at two sides of the axial direction of the inner ring and the outer ring, and the plurality of rolling bodies are uniformly distributed by the annular axial retainer;
the inner and outer rings in the radial direction form spherical raceways (909, 905, 906) that coincide with the centers of the mating steps, i.e., the spherical raceways of the inner and outer rings are spaced apart and coincide to form two spherical raceways of at least one step;
the outer ring forms a split outer ring matched with at least one of the two in the axial direction, and the outer diameters of the two outer rings are different;
the two outer sides of the split outer ring in the axial direction are partially coated with a distance part to form transmission rolling surfaces in the axial direction of the inner ring and the outer ring which are matched with each other, namely, the transmission rolling surface of the inner ring on one axial side of the spherical center is a conical rolling surface of which the conical rolling surface is matched with the transmission rolling surface of the outer ring on the other axial side of the spherical center, and the annular axial transmission rolling surfaces of the inner ring and the outer ring are correspondingly matched with the conical transmission rolling surfaces; such that the rolling bodies are configured as rolling bodies of said transmission rolling surface;
the stepped spherical raceways (909, 905) of the inner ring and the outer ring form a pair of ball rows (907, 908) which are axially distributed and matched with at least one of the ball rows, the ball rows are held at two sides of the ball center in the axial direction by a retainer, the diameter of each ball of each pair of the ball rows is slightly larger than a data value than the distance from the inner ring to the outer ring corresponding to the position of the ball, the ball rows are in point contact with the spherical raceways and are easy to roll, at least one part of load is firstly received, and the superposed spherical raceway surfaces (909, 906) of the inner ring and the outer ring are easy to be in sliding contact with the other part of load;
a plurality of bolt holes (9) matched with at least one split outer ring are formed in the outer periphery of the outer side of the split outer ring in the axial direction, the two outer rings are oppositely connected through the bolts (91) matched with at least one split outer ring, and the outer ring on one side of the split outer ring is in interference fit with the bearing box body;
the running clearance of the ball rows (907, 908) in the transmission device in the axial direction is pre-stressed by matching of a plurality of elastic elements matched on the plurality of bolts, and the running circumferential clearance of the transmission rolling bodies in the transmission device in the radial direction is adjusted by matching of a plurality of elastic elements (570, 660) matched on the retainer and automatic flexibility of the elastic elements on the plurality of bolts;
at least one of the rolling ratio and the flexible freedom of the rolling motion of at least one pair of ball rows (907, 908) of the inner ring and the outer ring and the sliding motion of the coincident spherical raceways (909, 906) of the inner ring and the outer ring under at least one external moment is configured to relatively control at least one motion of the precession motion and/or the support revolution motion of the inner ring and the outer ring in the transmission rolling surface motion;
the conical transmission rolling surfaces on two sides of the spherical centers of the inner ring and the outer ring are matched with the transmission device of the annular axial transmission rolling surface to drive the inner ring to rotate, the outer ring carries out precession motion towards the other direction under the external moment, and/or the conical transmission rolling surfaces on two sides of the spherical centers of the inner ring and the outer ring are matched with the transmission device of the annular axial transmission rolling surface to drive the outer ring to rotate, the inner ring carries out precession motion towards the other direction under the external moment, and/or the outer ring or the inner ring of one party carries out precession motion to drive the inner ring or the outer ring of the other party to carry out rotary motion towards the opposite direction, and/or the outer ring or the inner ring of one party carries out rotary motion to drive the inner ring or the outer ring of the other party to carry out relative supporting rotary motion;
the conical arrangement of the conical surfaces of the transmission rolling surfaces and the matching arrangement of the transmission rolling bodies relative to the precession movement realize the transmission ratio of the inner ring and the outer ring, and the transmission device is constructed to realize the change of at least one motion parameter between the driving and the output.
7. The active transmission device matched with at least one rolling body for transmission comprises the axial retainer and/or the planetary tray according to claim 2, wherein the rolling bodies are oppositely matched at two sides of the axial direction of the inner ring and the outer ring, and the rolling bodies are uniformly distributed by the annular axial retainer;
the inner and outer rings in the radial direction form spherical raceways (909, 905, 906) that coincide with the centers of the mating steps, i.e., the spherical raceways of the inner and outer rings are separated and coincide to form two spherical raceways of at least one step;
the outer ring in the axial direction forms a split outer ring matched with at least one of the two outer rings, and the outer diameters of the two outer rings are different;
the two outer sides of the split outer ring in the axial direction are partially coated with a distance part to form transmission rolling surfaces in the axial direction of the inner ring and the outer ring which are matched with each other, namely, the central axis of the conical transmission rolling surface of the outer ring on one axial side of the spherical center and the central axis of the conical transmission rolling surface of the inner ring on the other axial side of the spherical center are inclined relative to the central axis of the transmission shaft and the central axes of the inclined conical transmission rolling surfaces of the inner ring and the outer ring are crossed and parallel in motion, and the annular axial transmission rolling surfaces of the inner ring and the outer ring are matched with the inclined conical transmission rolling surfaces correspondingly; the rolling bodies are configured as rolling bodies of the transmission rolling surface;
the stepped spherical raceways (909, 905) of the inner ring and the outer ring form a pair of ball rows (907, 908) which are axially distributed and matched with at least one of the ball rows, the ball rows are held at two sides of the ball center in the axial direction by a retainer, the diameter of each ball of each pair of the ball rows is slightly larger than a data value than the distance from the inner ring to the outer ring corresponding to the position of the ball, the ball rows are formed to be in point contact with the spherical raceways so as to roll and firstly bear at least one part of load, and the superposed spherical raceway surfaces (909, 906) of the inner ring and the outer ring are easily in sliding contact and bear the other part of load;
a plurality of bolt holes (9) matched with at least one split outer ring are formed in the outer periphery of the outer side of the split outer ring in the axial direction, the two outer rings are oppositely connected through the bolts (91) matched with at least one split outer ring, and the outer ring on one side of the split outer ring is in interference fit with the bearing box body;
the running clearance of the ball rows in the transmission device in the axial direction is matched and pre-stressed by a plurality of elastic elements matched with the bolts, and the running circumferential clearance of the transmission rolling bodies in the transmission device in the radial direction is automatically flexibly adjusted by a plurality of elastic elements matched with the retainer and the elastic elements on the bolts;
the rolling motion of at least one pair of ball rows (907, 908) of the inner ring and the outer ring of the transmission rolling body and the sliding motion of the coincident spherical raceways (909, 906) of the inner ring and the outer ring are combined to form at least one compound motion corresponding to the precession motion and/or nutation motion of the inner ring and the outer ring relatively controlled in the motion of the transmission rolling surface in the operation of at least one of the slip ratio and the flexibility freedom;
the transmission device with the inclined conical transmission rolling surfaces on two sides of the spherical centers of the inner ring and the outer ring is matched with the annular axial transmission rolling surface to drive the inner ring to rotate, the outer ring performs precession motion towards the other direction, and/or the transmission device with the inclined conical transmission rolling surfaces on two sides of the spherical centers of the inner ring and the outer ring is matched with the annular axial transmission rolling surface to drive the outer ring to rotate, the inner ring performs precession motion towards the other direction, and/or the outer ring or the inner ring of one party performs precession motion to drive the inner ring or the outer ring of the other party to perform rotation motion towards the opposite direction;
the angular and conical arrangement of the central axis of the oblique cone of the transmission rolling surfaces relative to the compound movement effects a transmission ratio of the inner and outer rings, the transmission being configured such that a change in at least one motion parameter is effected between drive and output.
8. A stationary or passive transmission for bicycle (8) travel, comprising a stationary, passive transmission (800), an axial cage according to any of claims 1 to 6, characterized in that: the user steps on the outer ring of a transmission device (800) movably connected with a thrust bearing (810) of the pedal (820) with two feet to do rotary and precessional motion so as to drive the inner ring to rotate, and a cone gear (840) wheel fixedly connected with an output shaft (890) connected with the inner ring drives cone gears (850, 851) fixedly connected with wheels to drive the wheels (860,861) to run.
9. A transmission for an internal combustion engine of a stationary or passive type, comprising: a drive shaft assembly including a central drive shaft;
a cylindrical cylinder block having a longitudinal central axis with a central longitudinal opening for receiving the drive shaft, the cylindrical cylinder block further defining:
a plurality of combustion chambers each having an axis parallel to the central axis, the combustion chambers defined on a circle concentric with the longitudinal central axis, each of the combustion chambers having a generally cylindrical sidewall, a first closed end and a second open end, and an intake valve opening and an exhaust valve opening defined in the first closed end of each combustion chamber;
a coolant system including a plurality of coolant channels;
a plurality of intake passages, each in fluid communication with one of the intake valve openings;
and
a plurality of exhaust passages, each of which is in fluid communication with one of the plurality of exhaust valve openings;
a plurality of piston assemblies each having a piston received within one of the combustion chambers;
one end of each connecting rod is correspondingly connected with the piston spherical hinges;
a plurality of connecting rod bases, each of which is correspondingly connected with the other end spherical hinge of the plurality of connecting rods;
an annular base plate provided at an opposite end of the engine block and provided with a plurality of bosses, each of which is correspondingly connected with a plurality of link bases; and
a valve train including a plurality of intake valves and a plurality of exhaust valves, each of the valves being received in one of the valve openings within the combustion chamber;
the method is characterized in that:
the transmission of the internal combustion engine further includes: comprising a stationary transmission (1, 3, 7 a) according to any of claims 1-6, a passive transmission, an axial cage, the thrust bearings being arranged at opposite ends of the engine block, the annular chassis being arranged on one side of the thrust bearings, the transmission being arranged on the other side of the thrust bearings;
the engine central driving shaft is in running fit with a bearing arranged at the central longitudinal opening in the engine cylinder body and the inner ring of the transmission device;
the ignition expansion of the inner circulation of the cylinder drives each piston to do linear reciprocating circular motion, each connecting rod is pushed to do circular motion to drive the annular chassis and the thrust bearing respectively and sequentially, so that the outer ring of the transmission device is further driven to do rotary swinging precession motion, and the central driving shaft connected with the inner ring does rotary motion, so that the rotating speed and power output are realized.
10. Cycloidal reducer or cycloidal speed increaser (200) using a stationary transmission, comprising a stationary transmission according to any one of claims 1 to 5, an axial cage, characterized in that: the cycloidal reducer or speed increaser (200) comprising: first and second rolling bearings (201, 202), a cover wheel (203), a precession pin gear (210), a transmission device (1, 3, 7 a), a rigid ball body (207), an input shaft (206) and a shell (280);
the precession needle gear is arranged into a conical body (205), a needle groove is formed in the periphery of the conical body, the needle teeth (204) are movably matched in the needle groove, the precession needle gear is sleeved on the outer ring of one side of the transmission device and fixedly connected with the outer ring, and a pin (2088) is inserted into matching grooves (2050 and 1020) of the precession needle gear and the needle gear;
the inner periphery of the cover wheel is provided with internal teeth (2031), the axial center of the cover top is provided with an output shaft (2032), the inner bottom of the axial center of the cover wheel is provided with a spherical concave part (2030), and the outer periphery of the cover wheel is connected with the inner ring of the first rolling bearing (201) in a matching way;
the outer ring of the first rolling bearing is connected with the shell in a matching way;
the conical needle teeth (204) of the precession needle gear are matched in the internal teeth (2031) of the cover gear;
the outer axial center of the outer ring at one side of the transmission device is provided with a spherical concave part (103), and the steel ball body (207) is matched in the spherical concave parts (2030, 103) of the cover wheel and the outer ring of the transmission device;
one side of the input shaft is connected with an inner ring of the transmission device in a matching way, and the other side of the input shaft is fixedly connected with an inner ring of a second rolling bearing (202);
the outer ring of the second rolling bearing is fixedly connected with a shell (280);
the shell (280) is a half gourd ladle-shaped shell, a large-diameter inner chamber of the shell is connected with the first rolling bearing in a matching way, and a small-diameter inner chamber of the shell is connected with the second rolling bearing in a matching way, namely, the first rolling bearing, the second rolling bearing, the cover wheel, the precession needle gear, the transmission device and the shaft are wrapped by the two half gourd ladle-shaped shells and are radially connected with the shell by bolts; an elastic element (2011) is arranged between the outer edge (284) of the large-diameter inner chamber of the shell and the axial side end of the outer ring of the first rolling bearing; the elastic element is embedded into one of the grooves; the outer edge (285) of the small-diameter inner chamber of the shell wraps the axial side end of the outer ring of the second rolling bearing;
the input shaft drives the inner ring of the transmission device to rotate, the precession needle gear on the outer ring of the transmission device is driven to do revolution motion, the needle teeth of the precession needle gear are in oblique cross meshing with the inner teeth of the cover gear, the teeth in oblique cross meshing with the needle teeth are in progressive contact, and the precession needle gear revolves to do precession drive the output shaft of the cover gear to do deceleration motion.
11. Cycloidal reducer or cycloidal speed increaser (400) using a stationary transmission, comprising a stationary transmission according to any one of claims 1 to 5, an axial cage, characterized in that: the cycloidal reducer or speed increaser (400) comprising: the device comprises a precession cycloidal gear (401), a pinwheel (402), a transmission device (1, 3, 7 a), a first rolling bearing (405), a second rolling bearing (406), a driven wheel (404), an input shaft (407) and a shell (480);
the precession cycloid wheel is arranged in a conical cover shape, a plurality of through round parts (4012) are arranged at the bottom of the cover, conical external teeth (4011) are arranged on the periphery of the precession cycloid wheel, the inner periphery of the precession cycloid wheel is sleeved on the outer ring at one side of the transmission device (1, 3, 7 a) and fixedly connected with the outer ring, and a pin is inserted into matching grooves of the precession cycloid wheel and the transmission device;
one side of the inner periphery of the needle wheel is provided with a needle groove (4021), the needle teeth (403) are movably matched in the needle groove, the other side of the inner periphery is provided with an annular flange (4022), and the outer periphery of the annular flange is fixedly connected with the shell;
the inner circumference of the annular flange of the pinwheel is fixedly connected with the outer ring of a first rolling bearing (405);
an output shaft (4042) is arranged on one side of the driven wheel (404), a plurality of circular convex parts (4041) are arranged on the other side of the driven wheel, and the periphery of the circular convex parts is connected with an inner ring of the first rolling bearing (405) in a matched mode;
the circular convex parts (4041) of the driven wheel are matched in the through circular parts (4012) of the precession cycloidal gear, and the diameter of the through circular parts of the precession cycloidal gear is larger than that of the circular convex parts of the driven wheel;
one side of the input shaft (407) is connected with an inner ring of the transmission device in a matching way, the other side of the input shaft is connected with an inner ring of a second rolling bearing (406) in a matching way, and an outer ring of the second rolling bearing is fixedly connected with the shell (480);
the shell (480) is a half gourd ladle-shaped shell, a large-diameter inner chamber of the shell is connected with the outer diameter of the pinwheel in a matching way, and a small-diameter inner chamber of the shell is connected with the second rolling bearing in a matching way, namely, the pinwheel and the second rolling bearing are wrapped by the two half gourd ladle-shaped shells and are radially connected with the shell by bolts;
the input shaft drives the inner ring of the transmission device to rotate, the precession cycloid wheel on the outer ring of the transmission device is driven to revolve, the conical outer teeth of the precession cycloid wheel are in oblique line cross meshing with the needle teeth on the needle wheel, the teeth in oblique line cross meshing with the conical outer teeth are in progressive contact, the outer teeth in the revolution of the precession cycloid wheel are meshed with the needle teeth so as to drive the driven wheel to rotate at low speed, and the driven wheel forms at least one order of magnitude of rotation deceleration motion under the condition of difference of the tooth number of the conical outer teeth and the low speed rotation.
12. A fluid machine utilizing a stationary transmission, the fluid machine comprising: a central rotating shaft is arranged at the center of the rotary shaft,
a dome cover having a central opening and a plurality of circular holes evenly distributed around the central opening;
a round cup cylinder having a longitudinal central axis with a central longitudinal bottom opening for receiving said rotating shaft and a plurality of fluid openings in the cup wall, said dome fitting over the rim of the cylinder, the round cup cylinder further defining:
a plurality of chambers each having a central axis parallel thereto are disposed within the cylinder, each of the chambers having a generally cylindrical sidewall, a first closed end and a second open end, and a fluid inlet door opening and a fluid outlet door opening defined in the first closed end of each chamber, the plurality of chambers being defined on a circle concentric with the central axis, and the second open ends each communicating with the plurality of circular apertures of the dome cover;
a plurality of suction passages, each of which is in fluid communication with one of the intake door openings;
and
a plurality of discharge passages, each of which is in fluid communication with one of the plurality of discharge door openings and the plurality of fluid openings;
a plurality of piston assemblies each having a piston received within one of the chambers;
one end of each connecting rod is correspondingly connected with the piston spherical hinges;
a plurality of connecting rod bases, each of which is correspondingly connected with the other end spherical hinge of the plurality of connecting rods;
an annular base plate provided at an opposite end of the dome cover of the cylinder body, and provided with a plurality of bosses, each of which is correspondingly coupled with a plurality of link bases; and
an intake and exhaust door mechanism including a plurality of intake doors and a plurality of exhaust doors, each of the intake doors being received in one of the intake and exhaust door openings within or outside the chamber;
the method is characterized in that:
the transmission device of the fluid machine further includes: comprising a steady transmission (1, 3, 7 a) according to any of claims 1 to 5, an axial cage (500); the thrust bearing is arranged at the opposite end of the cylinder body of the fluid machine, the annular chassis is arranged on one side of the thrust bearing, and the transmission device is arranged on the other side of the thrust bearing;
the central rotating shaft of the fluid machine is in rotating fit with a bearing penetrating through the central longitudinal bottom opening of the cylinder body of the fluid machine, a bearing arranged at the central opening of the dome cover and the inner ring of the transmission device;
the central rotating shaft of the fluid machine is driven to drive the inner ring of the transmission device to rotate, the outer ring is driven to do rotational and swinging precession motion, the thrust bearing and the annular chassis are pushed to drive each connecting rod to respectively and sequentially perform cyclic motion, each piston is driven to linearly reciprocate to perform cyclic motion, and the fluid is sucked → discharged from the door inlet and outlet mechanism.
13. Planetary reducer and/or planetary speed increaser (7) with opposed transmission elements of reducer or speed increaser combined with bearings and/or transmission, comprising a stable, passive transmission, axial cage according to any of claims 1 to 6, characterized in that:
the planetary reducer (7) is tightly combined on the shell by an axial inner gear ring sleeve (700), one axial side of the inner gear ring sleeve is provided with a first planetary gear set (741) which is driven by external power and is equally combined by a plurality of elements on a tray (731), the other axial side of the inner gear ring sleeve is provided with a second planetary gear set (742) which is equally combined by a plurality of elements on a force output side on a tray (732), a central sun driven wheel (720) is arranged between the force output side and the force input side, and the tray (731,732) of the opposite planetary transmission elements (741, 742) is supported and floated in the period of time by the force input shaft (751) and the force output shaft (752), the inner gear ring sleeve and the sun driven wheel; when the power of the input side drives the first planetary transmission element of the input shaft connected with the tray, the sun driven wheel can be driven to rotate, so as to drive the second planetary transmission element of the output side to rotate and drive the output shaft connected with the tray to output power, and the opposite planetary transmission elements revolve along the central rotation axis along the track of the inner gear sleeve under the axial diameter ratio of each group of elements.
14. -planetary reducer and/or planetary speed increaser, and/or central sun-split opposed reducer and/or speed increaser (6) with opposed transmission elements of the reducer or speed increaser of the combined bearing and/or transmission, comprising a passive transmission, an axial cage according to any of claims 2 or 6, characterised in that:
the planetary reducer is tightly combined on a shell by an axial inner gear ring sleeve, one axial side of the inner gear ring sleeve is provided with a first planetary element set formed by a plurality of elements on a power output side in an equal division mode and combined on a tray, the other axial side of the inner gear ring sleeve is provided with a second planetary element set formed by a plurality of elements on a driven side in an equal division mode and combined on the tray, a central sun wheel is provided with a power input side driven by external power and arranged between the driven side and the power output side, and the tray of the opposite planetary transmission elements is supported and floated in the period by the power output shaft, the driven side, the inner gear ring sleeve and the sun wheel power input side; when the input shaft drives the sun wheel to rotate at the input side, the tray of the second planetary transmission element at the driven side can be driven to rotate, so that the first planetary transmission element at the output side is driven to rotate to drive the output shaft connected with the tray to output power, and the opposite planetary transmission elements revolve along the central rotation axis along the track of the inner gear sleeve under the axial diameter ratio of each group of elements;
and/or said combination bearing and/or transmission means are constructed in such a way that at least two internally central sun gears (620) are axially split, i.e. a set of transmission elements (630) is interposed between the two sun gears (620), the outer spherical rolling surfaces (909a, 909b) of each set of sun gears (621, 622) in the radial direction are in rolling and sliding motion with the ball rows (907, 908) and the inner spherical raceways (905, 906) of the split inner ring sleeves, said additional pair of transmission elements (680) are fitted on both outer sides of the opposing split sun gears (620), said one outer side surrounds their split inner ring sleeves (600) with a through-going hole of the common centre line of rotation, said input side (AX) is in close fitting connection with the inner diameter of the sun gear (621) on one side, the output side (AF) is in close fitting connection with the inner diameter of the sun gear (620) on the other side, they are made integral by screws axially connecting the split inner ring sleeves, and are formed in the transmission and/or transmission of the split sun gears; wherein the motion of the auxiliary pair of transmission elements in the axial side is a rolling motion of rolling elements, and the transmission rolling surfaces of the axial sides of the split inner toothed ring sleeve (600) and the sun wheel (620) of the bearing and/or device are configured in the shape of rolling elements, the two sides of the middle of the split sun wheel forming annular gears and/or transmission rolling surfaces, the central set of transmission elements (630) being formed as small gear sets and/or rolling elements between the split sun wheels, the central small gear sets and/or rolling elements being distributed as common by a carrier (631), the central small gear sets and/or rolling elements forming a configuration with concentric integration of the size of the steps of each transmission element, i.e. the stepped transmission elements (632) forming large diameter ends (6320) and small diameter ends (6321), the small gear sets each forming gears with different numbers of teeth of the large diameter ends and the small diameter ends, the annular gears (625, the annular gears (626) being distributed uniformly by an axial cage and/or planetary carrier (63) annularly arranged between the two sides of the split sun wheel (620) with the annular gears (625, the other side being in that the annular ring gear (626) is in contact with the large diameter end (632) of the split ring (626), the annular ring gear (632) of the split sun wheel (626); and/or the tray forms a screw through hole which extends to the inner gear ring sleeve (600) in the radial direction and is not contacted with the tray by a screw (91) and is not fixed in rotation between the two adjacent parts, and/or a clamping ring (690) is further arranged between the split inner gear ring sleeves (601, 602) and the radial outer diameter of the tray (631) of the central transmission element group (630), wherein the clamping ring (690) forms two semicircular rings and is used for fixing the tray by an external force; the central sun-split opposing reduction gear and/or speed increaser (6) has a stepped transmission element (632) which is designed such that a transmission ratio of at least one order of magnitude is formed between the input side (AX) and the output side (AF).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211313259.2A CN115638186A (en) | 2020-08-15 | 2020-08-15 | Stable, passive and active combined bearing and/or transmission device and retainer, and equipment machine using various transmission devices |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211313259.2A CN115638186A (en) | 2020-08-15 | 2020-08-15 | Stable, passive and active combined bearing and/or transmission device and retainer, and equipment machine using various transmission devices |
| CN202010821664.XA CN112112894B (en) | 2020-08-15 | 2020-08-15 | Rolling joint bearing with angular motion freedom |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010821664.XA Division CN112112894B (en) | 2020-08-15 | 2020-08-15 | Rolling joint bearing with angular motion freedom |
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| Publication Number | Publication Date |
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| CN115638186A true CN115638186A (en) | 2023-01-24 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211313259.2A Pending CN115638186A (en) | 2020-08-15 | 2020-08-15 | Stable, passive and active combined bearing and/or transmission device and retainer, and equipment machine using various transmission devices |
| CN202111007956.0A Pending CN114076147A (en) | 2020-08-15 | 2020-08-15 | Bearing, precession bearing and precession bearing gyro, and gyro precession type active stabilization device using precession bearing gyro |
| CN202110786478.1A Pending CN114076146A (en) | 2020-08-15 | 2020-08-15 | Bearing, and rocking bearing device for reciprocating motion |
| CN202010821664.XA Active CN112112894B (en) | 2020-08-15 | 2020-08-15 | Rolling joint bearing with angular motion freedom |
| CN202110657765.2A Pending CN114076145A (en) | 2020-08-15 | 2020-08-15 | Bearing, and yaw bearing with controllable angular offset, and bearing device for wheel |
Family Applications After (4)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111007956.0A Pending CN114076147A (en) | 2020-08-15 | 2020-08-15 | Bearing, precession bearing and precession bearing gyro, and gyro precession type active stabilization device using precession bearing gyro |
| CN202110786478.1A Pending CN114076146A (en) | 2020-08-15 | 2020-08-15 | Bearing, and rocking bearing device for reciprocating motion |
| CN202010821664.XA Active CN112112894B (en) | 2020-08-15 | 2020-08-15 | Rolling joint bearing with angular motion freedom |
| CN202110657765.2A Pending CN114076145A (en) | 2020-08-15 | 2020-08-15 | Bearing, and yaw bearing with controllable angular offset, and bearing device for wheel |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114427573B (en) * | 2022-03-07 | 2022-12-27 | 姜虹 | Retainer assembly, flat thrust bearing, radial bearing, and tapered radial thrust bearing |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2983558A (en) * | 1958-06-27 | 1961-05-09 | Marion F Rudy | Micro-ball joint |
| GB945930A (en) * | 1962-11-05 | 1964-01-08 | Southwest Products Co | Improvements in or relating to bearings and a method of making same |
| US3698251A (en) * | 1971-08-12 | 1972-10-17 | Ambac Ind | Thrust retainer for spherical race ball bearings |
| US20070165975A1 (en) * | 2005-12-12 | 2007-07-19 | John Brodowski | Axial, rotational and angular motion ball bearing |
| JP2009008193A (en) * | 2007-06-29 | 2009-01-15 | Hiihaisuto Seiko Kk | Retainer of spherical roller bearing |
| DE102007034570A1 (en) * | 2007-07-25 | 2009-01-29 | Schaeffler Kg | Antifriction bearing for use in mixer drive of mixer drum, has inner race with outer contour formed in concave shape, and outer race with inner contour formed concave complementary to outer contour |
| CN201925338U (en) * | 2010-05-31 | 2011-08-10 | 江阴市富贝轴承有限公司 | External thread type anticorrosion enhanced knuckle bearing |
| CN104389899B (en) * | 2014-10-13 | 2018-02-09 | 北京控制工程研究所 | A kind of band preloads roller oscillating bearing |
| CN106089997A (en) * | 2016-08-22 | 2016-11-09 | 怀宁吉利来精密机械科技有限公司 | A kind of manufacturing process of PTFE material water conservancy oscillating bearing |
-
2020
- 2020-08-15 CN CN202211313259.2A patent/CN115638186A/en active Pending
- 2020-08-15 CN CN202111007956.0A patent/CN114076147A/en active Pending
- 2020-08-15 CN CN202110786478.1A patent/CN114076146A/en active Pending
- 2020-08-15 CN CN202010821664.XA patent/CN112112894B/en active Active
- 2020-08-15 CN CN202110657765.2A patent/CN114076145A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| CN112112894A (en) | 2020-12-22 |
| CN114076145A (en) | 2022-02-22 |
| CN114076147A (en) | 2022-02-22 |
| CN114076146A (en) | 2022-02-22 |
| CN112112894B (en) | 2022-10-21 |
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