CN110821978A - Eight steel ball rzeppa constant velocity joints of wide-angle high efficiency - Google Patents
Eight steel ball rzeppa constant velocity joints of wide-angle high efficiency Download PDFInfo
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- CN110821978A CN110821978A CN201911309759.7A CN201911309759A CN110821978A CN 110821978 A CN110821978 A CN 110821978A CN 201911309759 A CN201911309759 A CN 201911309759A CN 110821978 A CN110821978 A CN 110821978A
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- 229910000831 Steel Inorganic materials 0.000 title claims abstract description 122
- 239000010959 steel Substances 0.000 title claims abstract description 122
- 238000005096 rolling process Methods 0.000 claims description 39
- 230000007704 transition Effects 0.000 claims description 3
- 230000005540 biological transmission Effects 0.000 abstract description 7
- 238000010276 construction Methods 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 230000008407 joint function Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22303—Details of ball cages
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22309—Details of grooves
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The invention discloses a large-angle high-efficiency eight-steel-ball rzeppa constant velocity universal joint.A bell housing inner raceway and a star sleeve outer raceway are conjugated and are both composed of two sections of tangent reverse arcs; the center line of the first pair of inner raceways is positioned outside the center line of the inner spherical surface, the angle between the connecting line of the tangent point A of the center track A of the steel ball I and the center of the inner circular arc I and the center line of the inner raceways is 2-4 degrees, the center lines of the second pair of inner raceways and the fourth pair of inner raceways are superposed with the center line of the inner spherical surface, and the angle between the connecting line of the tangent point A of the center track A of the steel balls II and IV and the center of the inner circular arc I and the center line of the inner raceways is; the center line of the third inner raceway is positioned at the inner side of the center line of the inner spherical surface, and the angle between the connecting line of the tangent point A of the center track A of the steel ball III and the center of the inner arc I and the center line of the inner raceway is 9-11 degrees. The angle of the invention can reach 52 degrees, the intensity is high, the transmission efficiency is high, the structure is more compact, the weight is lighter, and the invention can be suitable for vehicles with smaller requirements on the turning radius of the vehicle.
Description
Technical Field
The invention belongs to the field of automobile parts, and relates to a wide-angle high-efficiency eight-steel-ball rzeppa constant velocity universal joint.
Background
High performance constant velocity universal drive shaft assemblies for passenger vehicles are typically constructed of a fixed joint, a slip joint and an intermediate shaft connected between the joints.
In general, a universal joint functions to transmit rotational power (torque) between two rotating shafts that meet each other at an angle. In the case of a propeller shaft having a small power transmission angle, a hook type joint, a flexible joint, or the like is used, and in the case of a drive shaft of a front wheel drive vehicle having a large power transmission angle, a constant velocity joint is used. The constant velocity joint is mainly used for an axle of an independent suspension type front wheel drive vehicle because the constant velocity joint can reliably transmit power at a constant velocity even when an angle between a drive shaft and a driven shaft is large. When viewed from the axis, the tripod constant velocity joint is disposed at an inboard end of the axis facing the engine, and the birfield joint is disposed at an outboard end of the axis facing the tire. The high-performance constant velocity universal drive shaft assembly is required to stably transmit power, and is also required to have reliable strength and durability.
With the shortage of global resources and the increasing attention of governments on environmental protection, the light weight of automobiles has become a necessary trend in the development of the automobile industry at present.
The conventional six-steel-ball-cage type constant velocity universal joint has relatively small steel number, large sizes of a universal joint bell-shaped shell and a star sleeve channel, and small size of a reference circle of a middle shaft spline connected with the star sleeve, so that the conventional six-steel-ball-cage type constant velocity universal joint has large volume and mass and large maximum angle, if the maximum angle of an RZ joint can only reach 47 degrees, the maximum angle of an UF joint can only reach 50 degrees, and the capacity of transmitting torque is limited. The smaller the angle of the universal joint is, the smaller the turning radius of the vehicle is, and the higher the vehicle performance is, but the smaller the angle is, the smaller the geometric dimension needs to be greatly reduced in the conventional six-steel-ball rzeppa constant velocity universal joint, which directly results in that the strength and the durability can not meet the design requirements. Therefore, the traditional six-steel-ball cage type constant velocity universal joint cannot meet the use requirement of a vehicle with a small turning radius requirement. In addition, the hook tracks of the outer race and the inner race of the conventional six-ball rzeppa constant velocity universal joint are the same, and because the raceways of the two parts are eccentric relative to the spherical surface, the outer side of the outer spherical surface of the cage can extrude the outer side of the inner spherical surface of the outer race under the condition of a large angle, so that internal heat generation is caused, and the durability and the transmission efficiency are reduced.
Disclosure of Invention
The invention aims to solve the problems in the prior art, and provides a large-angle high-efficiency eight-steel-ball rzeppa constant velocity universal joint, which has an angle of 52 degrees, high strength, high transmission efficiency, a more compact structure, lighter weight, lower matching cost and can be used for vehicles with smaller requirements on turning radius of the vehicles.
In order to achieve the purpose, the technical solution of the invention is as follows: a large-angle high-efficiency eight-steel-ball rzeppa constant velocity universal joint comprises an outer bell housing provided with an inner cavity, an inner star sleeve positioned in the inner cavity of the outer bell housing, an annular retainer and 8 steel balls: steel ball I, steel ball II, steel ball III, steel ball IV, steel ball V, steel ball VI, steel ball VII and steel ball VIII; 8 steel balls which are kept in an angular bisector plane by an annular retainer with eight windows uniformly distributed are arranged between the roller path of the star-shaped sleeve and the roller path of the outer shell, and the roller paths are matched in a transition fit; the inner wall of the bell-shaped shell and the inner wall of the annular retainer form a group of spherical pairs, the inner wall of the annular retainer and the outer wall of the star-shaped sleeve form another group of spherical pairs, and the two groups of spherical pairs are in clearance fit; the surface of the inner cavity of the bell-shaped shell is provided with 8 inner roller ways: the outer surface of the star-shaped sleeve is provided with 8 outer rolling ways at the positions corresponding to the inner rolling ways: the rolling bearing comprises an outer rolling path I, an outer rolling path II, an outer rolling path III, an outer rolling path IV, an outer rolling path V, an outer rolling path VI, an outer rolling path VII and an outer rolling path VIII, wherein 8 inner rolling paths and 8 outer rolling paths are conjugated and are composed of two sections of tangent reverse arcs; the spherical surface of the inner cavity of the bell-shaped shell is an inner spherical surface, the spherical surface of the outer surface of the star-shaped sleeve is an outer spherical surface, and the central line of the inner spherical surface is superposed with the central line of the outer spherical surface; when the steel ball rolls along the inner raceway, the central track A of the steel ball consists of two sections of tangent reverse inner circular arcs I and outer circular arcs II, and the tangent point is A; when the steel ball rolls along the outer raceway, the central track B of the steel ball consists of two sections of tangent reverse inner side circular arcs III and outer side circular arcs IV, and the tangent point is B; the central tracks A and B of the steel balls are arranged in a mirror image mode relative to the central line of the inner or outer spherical surface; the center line of a first pair of inner raceways formed by the inner raceway I and the inner raceway V is positioned outside the center line of the inner spherical surface, the distance is e1, the angle between the connecting line of the tangent point A of the center track A of the steel ball I and the center of the inner circular arc I and the center line of the inner raceway is 2-4 degrees, and the offset distance L1 exists between the center of the inner circular arc I of the center track A of the steel ball I and the longitudinal axis of the part; the center lines of a second pair of inner raceways formed by an inner raceway II and an inner raceway VI and the center line of a fourth pair of inner raceways formed by an inner raceway IV and an inner raceway VIII are superposed with the center line of an inner spherical surface, the angle between the connecting line of the tangent point A of the center track A of the steel ball II and the steel ball IV and the center of the inner side circular arc I and the center line of the inner raceway is 4-6 degrees, and the offset distance L3 exists between the center of the inner side circular arc I of the center track A of the steel ball II and the steel ball IV relative to the longitudinal axis of the part; the center line of a third inner raceway formed by the inner raceway III and the inner raceway VII is positioned on the inner side of the center line of the inner spherical surface, the distance is e3, the angle between the connecting line of the tangent point A of the center track A of the steel ball III and the center of the inner arc I and the center line of the inner raceway is 9-11 degrees, and the offset L2 exists between the center of the inner arc I of the center track A of the steel ball III and the longitudinal axis of the part; the center line of a first pair of outer raceways formed by the outer raceway I and the outer raceway V is positioned on the inner side of the center line of the outer spherical surface, the distance is e2, the angle between the connecting line of the tangent point B of the center track B of the steel ball I and the center of the outer arc IV and the center line of the outer raceway is 2-4 degrees, and the offset distance L1 exists between the center of the outer arc IV of the center track B of the steel ball I and the longitudinal axis of the part; the center lines of a second pair of outer raceways formed by an outer raceway II and an outer raceway VI and the center lines of a fourth pair of outer raceways formed by an outer raceway IV and an outer raceway VIII are superposed with the center line of an outer spherical surface, the angle between the connecting line of the tangent point B of the center track B of the steel ball II and the steel ball IV and the center line of the outer circular arc IV and the center line of the outer raceway is 4-6 degrees, and the offset distance L3 exists between the center of the outer circular arc IV of the center track B of the steel ball II and the steel ball IV relative to the longitudinal axis of the; the center line of a third pair of outer raceways formed by the outer raceway III and the outer raceway VII is located on the outer side of the center line of the outer spherical surface, the distance is e4, the angle between the connecting line of the tangent point B of the center track B of the steel ball III and the center of the outer arc IV and the center line of the outer raceway is 9-11 degrees, and the offset distance L2 exists between the center of the outer arc IV of the center track B of the steel ball III and the longitudinal axis of the part.
Further preferably, e1= e2= (0.20-0.27) d0, and d0 is a steel ball diameter.
Further preferably, when the universal joint angle is 0 °, the distance between the centers of the two steel balls in each pair of raceways is the steel ball center diameter d1, d1= (3.9-4.3) d 0.
Further preferably, the L1/L2/L3= (0.20-0.27) d 0.
Further preferably, the radii R1= (1.65-1.85) × d0 of the outer arc ii and the inner arc iii of the first pair of inner and outer raceways; the radiuses R2= (0.85-1.0) × d0 of the outer circular arc II and the inner circular arc III of the third pair of inner and outer raceways; and the radiuses R3= (1.5-1.7) × d0 of the outer circular arc II and the inner circular arc III of the second inner raceway and the fourth outer raceway.
Further preferably, the outer diameter D = (5.6 to 6.0) × D0 of the outer bell housing.
Further preferably, the star sleeve is connected with the driving shaft through an involute spline, and a full-through type middle snap ring positioning structure or an end snap ring positioning structure with a positioning table is adopted; the outer end of the outer shell is provided with a thread with a locking function.
The outer race and the inner race of the present invention each include eight raceways, which results in a reduced envelope size, maintained strength and durability, and reduced mass compared to a six-raceway universal joint. The inner race centers of the inner race and outer race are first on the right side of the spherical centerline, third on the left side of the spherical centerline, and second and fourth on the spherical centerline. The first pair and the third pair are arranged by offsetting to fix the steel ball on the central line of the inner spherical surface in a hinged manner and drive the steel ball to move in the raceway, and the second pair and the fourth pair are not offset and follow up by means of the angle change movement of the first pair and the third pair of the steel balls. Because the first pair of raceways and the third pair of raceways are arranged in a biased manner, the inward force and the outward force of the retainer are equal, and the excessive extrusion and abrasion of the outer side of the spherical surface of the retainer are avoided, so that the transmission efficiency is improved, and the maximum working angle of the universal joint can reach 52 degrees. In a word, the angle of the invention can reach 52 degrees, the intensity is high, the transmission efficiency is high, the structure is more compact, the weight is lighter, the invention can be suitable for the vehicle with smaller turning radius requirement, and the matching cost is lower.
Drawings
FIG. 1 is an axial cross-sectional schematic view of the present invention;
FIG. 2 is a schematic structural view of a first pair of raceways of the outer race of the present invention;
FIG. 3 is a schematic structural view of a third pair of raceways of the outer race of the present invention;
FIG. 4 is a schematic structural view of the second and fourth pairs of raceways of the outer race of the present invention;
FIG. 5 is a schematic view of the construction of the first pair of raceways of the inner race of the present invention;
FIG. 6 is a schematic structural view of a third pair of raceways of the inner race of the present invention;
FIG. 7 is a schematic diagram of the construction of the second and fourth pairs of raceways of the inner race of the present invention;
FIG. 8 is a view of the manner in which the annular cage and the inner race of the present invention are assembled;
FIG. 9 is a 52 ° angle lower assembly view of the first inner and outer races of the invention;
FIG. 10 is a 52 degree angle of the third pair of inner and outer raceways for the present invention;
FIG. 11 is a 52 ° angle lower assembly of the second and fourth inner and outer races of the invention;
FIG. 12 shows the state of the ball bearing in the ring-shaped cage based on the offset of the raceway.
Detailed Description
The invention is further described with reference to specific examples.
As shown in fig. 1 to 11, the present embodiment includes an outer race 1 provided with an inner cavity, an inner race 2 located in the inner cavity of the outer race 1, an annular retainer 4, and 8 steel balls: steel ball I31, steel ball II 32, steel ball III 33, steel ball IV 34, steel ball V35, steel ball VI 36, steel ball VII 37 and steel ball VIII 38. 8 steel balls which are kept in an angular bisector plane by an annular retainer 4 uniformly distributed with eight windows are arranged between the raceway of the star-shaped sleeve 2 and the raceway of the outer shell 1, and the raceway matching is transition matching. The inner wall of the outer shell 1 and the inner wall of the annular retainer 4 form a group of spherical pairs, the inner wall of the annular retainer 4 and the outer wall of the star-shaped sleeve 2 form another group of spherical pairs, and the two groups of spherical pairs are in clearance fit. 8 inner raceways are arranged on the surface of the inner cavity of the outer shell 1: the outer surface of the star-shaped sleeve 2 is provided with 8 outer rolling ways at the positions corresponding to the inner rolling ways: the three-dimensional bearing comprises an outer rolling path I, an outer rolling path II, an outer rolling path III, an outer rolling path IV, an outer rolling path V, an outer rolling path VI, an outer rolling path VII and an outer rolling path VIII, wherein 8 inner rolling paths and 8 outer rolling paths are conjugated and are formed by two sections of tangent reverse arcs. The spherical surface of the inner cavity of the outer shell 1 is an inner spherical surface, the spherical surface of the outer surface of the inner star-shaped sleeve 2 is an outer spherical surface, and the central line 11 of the inner spherical surface is superposed with the central line 21 of the outer spherical surface. When the steel ball rolls along the inner raceway, the central track A of the steel ball consists of two tangent reverse inner circular arcs I51 and outer circular arcs II 52, and the tangent point is A. When the steel ball rolls along the outer raceway, the central track B of the steel ball consists of two sections of tangent reverse inner side circular arcs III 53 and outer side circular arcs IV 54, and the tangent point is B. The ball center trajectories a and B are mirror image arrangements with respect to the inner or outer spherical surface center line 11/21. A first pair of inner raceway center lines 121 formed by the inner raceway I and the inner raceway V are located on the outer side of an inner spherical surface center line 11, the distance is e1, the angle between a connecting line 61 of a tangent point A of a center track A of the steel ball I31 and a center C of an inner side circular arc I51 and the inner raceway center line 121 is any angle of 2-4 degrees, the best angle is 3 degrees, and the offset distance L1 exists between the center C of the inner side circular arc I51 of the center track A of the steel ball I31 and a longitudinal axis 7 of a part. The center lines of a second pair of inner roller paths 122 consisting of an inner roller path II and an inner roller path VI and a fourth pair of inner roller paths 124 consisting of an inner roller path IV and an inner roller path VIII are superposed with the center line 11 of the inner spherical surface, the angle between the connecting line 63 of the tangent point A of the center track A of the steel ball II 32 and the steel ball IV 34 and the center C of the inner circular arc I51 and the center line 11 of the inner roller path is any angle of 4-6 degrees, the best angle is 5 degrees, and the offset distance L3 exists between the center of the inner circular arc I51 of the center track A of the steel ball II 32 and the steel ball IV 34 relative to the longitudinal axis 7 of the. The third pair of inner raceway center lines 123 consisting of the inner raceway III and the inner raceway VII are located on the inner side of the inner spherical surface center line 11, the distance is e3, the angle between the connecting line 63 of the tangent point A of the center track A of the steel ball III 33 and the center C of the inner circular arc I51 and the inner raceway center line 11 is any angle of 9-11 degrees, the best angle is 10 degrees, and the offset distance L2 exists between the center C of the inner circular arc I51 of the center track A of the steel ball III 33 and the longitudinal axis 7 of the part. A first pair of outer raceway center lines 221 formed by the outer raceway I and the outer raceway V are located on the inner side of an outer spherical surface center line 21, the distance is e2, the angle between a connecting line 81 of a tangent point B of a center track B of the steel ball I31 and a center D of the outer arc IV 54 and the outer raceway center line 221 is any angle of 2-4 degrees, the best angle is 3 degrees, and the offset distance L1 exists between the center D of the outer arc IV 54 of the center track B of the steel ball I31 and a longitudinal axis 7 of a part. The second pair of outer raceway center lines 222 formed by the outer raceway II and the outer raceway VI and the fourth pair of outer raceway center lines 224 formed by the outer raceway IV and the outer raceway VIII are superposed with the outer spherical surface center line 21, the angle between the connecting line 83 of the tangent point B of the center track B of the steel ball II 32 and the steel ball IV 34 and the center D of the outer arc IV 54 and the outer raceway center line 21 is any angle of 4-6 degrees, the optimal angle is 5 degrees, and the offset distance L3 exists between the center D of the outer arc IV 54 of the center track B of the steel ball II 32 and the steel ball IV 34 relative to the longitudinal axis 7 of the part. And a third outer raceway center line 83 formed by the outer raceway III and the outer raceway VII is positioned on the outer side of the outer spherical surface center line 21, the distance is e4, the angle between a connecting line 83 between a tangent point B of a center track B of the steel ball III 33 and the center D of the outer arc IV 54 and the outer raceway center line 21 is any angle of 9-11 degrees, the best angle is 10 degrees, and the offset distance L2 exists between the center D of the outer arc IV 54 of the center track B of the steel ball III 33 and the longitudinal axis 7 of the part. Preferably, e1= e2= (0.20-0.27) d0, and d0 is the diameter of the steel ball. Preferably, when the universal joint angle is 0 degrees, the distance between the centers of the two steel balls in each pair of raceways is the steel ball center diameter d1, d1= (3.9-4.3) d 0. Preferably, the L1/L2/L3= (0.20-0.27) d 0. Preferably, the radii R1= (1.65-1.85) × d0 of the outer arc ii 52 and the inner arc iii 53 of the first pair of inner and outer raceways; the radiuses R2= (0.85-1.0) × d0 of the outer circular arc II 52 and the inner circular arc III 53 of the third pair of inner and outer raceways; and the radiuses R3= (1.5-1.7) × d0 of the outer circular arc II 52 and the inner circular arc III 53 of the second inner raceway and the fourth inner raceway. Preferably, the outer diameter D = (5.6-6.0) × D0 of the outer bell housing 1. Preferably, the star sleeve 2 is connected with the driving shaft 9 through an involute spline, and a full-through type middle snap ring positioning structure or an end snap ring positioning structure with a positioning table is adopted. The outer shell 1 is connected with the hub through an involute spline, and the thread at the outermost end of the outer shell 1 has a locking function.
As shown in figure 12, when the parts in the universal joint rotate clockwise, the steel balls II 32, IV 36, VI 34 and VIII 38 follow the steel balls I31, III 33, V35 and VII 37 to move.
The above-described embodiments are merely preferred and illustrative, and not restrictive, and any modifications, equivalents, improvements, etc., which come within the spirit and principles of the invention are intended to be included within the scope of the invention.
Claims (10)
1. The utility model provides an eight steel ball rzeppa constant velocity universal joints of wide-angle high efficiency which characterized in that: the device comprises an outer bell shell with an inner cavity, an inner star sleeve positioned in the inner cavity of the outer bell shell, an annular retainer and 8 steel balls: steel ball I, steel ball II, steel ball III, steel ball IV, steel ball V, steel ball VI, steel ball VII and steel ball VIII; 8 steel balls which are kept in an angular bisector plane by an annular retainer with eight windows uniformly distributed are arranged between the roller path of the star-shaped sleeve and the roller path of the outer shell, and the roller paths are matched in a transition fit; the inner wall of the bell-shaped shell and the inner wall of the annular retainer form a group of spherical pairs, the inner wall of the annular retainer and the outer wall of the star-shaped sleeve form another group of spherical pairs, and the two groups of spherical pairs are in clearance fit; the surface of the inner cavity of the bell-shaped shell is provided with 8 inner roller ways: the outer surface of the star-shaped sleeve is provided with 8 outer rolling ways at the positions corresponding to the inner rolling ways: the rolling bearing comprises an outer rolling path I, an outer rolling path II, an outer rolling path III, an outer rolling path IV, an outer rolling path V, an outer rolling path VI, an outer rolling path VII and an outer rolling path VIII, wherein 8 inner rolling paths and 8 outer rolling paths are conjugated and are composed of two sections of tangent reverse arcs; the spherical surface of the inner cavity of the bell-shaped shell is an inner spherical surface, the spherical surface of the outer surface of the star-shaped sleeve is an outer spherical surface, and the central line of the inner spherical surface is superposed with the central line of the outer spherical surface; when the steel ball rolls along the inner raceway, the central track A of the steel ball consists of two sections of tangent reverse inner circular arcs I and outer circular arcs II, and the tangent point is A; when the steel ball rolls along the outer raceway, the central track B of the steel ball consists of two sections of tangent reverse inner side circular arcs III and outer side circular arcs IV, and the tangent point is B; the central tracks A and B of the steel balls are arranged in a mirror image mode relative to the central line of the inner or outer spherical surface; the center line of a first pair of inner raceways formed by the inner raceway I and the inner raceway V is positioned outside the center line of the inner spherical surface, the distance is e1, the angle between the connecting line of the tangent point A of the center track A of the steel ball I and the center of the inner circular arc I and the center line of the inner raceway is 2-4 degrees, and the offset distance L1 exists between the center of the inner circular arc I of the center track A of the steel ball I and the longitudinal axis of the part; the center lines of a second pair of inner raceways formed by an inner raceway II and an inner raceway VI and the center line of a fourth pair of inner raceways formed by an inner raceway IV and an inner raceway VIII are superposed with the center line of an inner spherical surface, the angle between the connecting line of the tangent point A of the center track A of the steel ball II and the steel ball IV and the center of the inner side circular arc I and the center line of the inner raceway is 4-6 degrees, and the offset distance L3 exists between the center of the inner side circular arc I of the center track A of the steel ball II and the steel ball IV relative to the longitudinal axis of the part; the center line of a third inner raceway formed by the inner raceway III and the inner raceway VII is positioned on the inner side of the center line of the inner spherical surface, the distance is e3, the angle between the connecting line of the tangent point A of the center track A of the steel ball III and the center of the inner arc I and the center line of the inner raceway is 9-11 degrees, and the offset L2 exists between the center of the inner arc I of the center track A of the steel ball III and the longitudinal axis of the part; the center line of a first pair of outer raceways formed by the outer raceway I and the outer raceway V is positioned on the inner side of the center line of the outer spherical surface, the distance is e2, the angle between the connecting line of the tangent point B of the center track B of the steel ball I and the center of the outer arc IV and the center line of the outer raceway is 2-4 degrees, and the offset distance L1 exists between the center of the outer arc IV of the center track B of the steel ball I and the longitudinal axis of the part; the center lines of a second pair of outer raceways formed by an outer raceway II and an outer raceway VI and the center lines of a fourth pair of outer raceways formed by an outer raceway IV and an outer raceway VIII are superposed with the center line of an outer spherical surface, the angle between the connecting line of the tangent point B of the center track B of the steel ball II and the steel ball IV and the center line of the outer circular arc IV and the center line of the outer raceway is 4-6 degrees, and the offset distance L3 exists between the center of the outer circular arc IV of the center track B of the steel ball II and the steel ball IV relative to the longitudinal axis of the; the center line of a third pair of outer raceways formed by the outer raceway III and the outer raceway VII is located on the outer side of the center line of the outer spherical surface, the distance is e4, the angle between the connecting line of the tangent point B of the center track B of the steel ball III and the center of the outer arc IV and the center line of the outer raceway is 9-11 degrees, and the offset distance L2 exists between the center of the outer arc IV of the center track B of the steel ball III and the longitudinal axis of the part.
2. The high angle, high efficiency eight steel ball, rzeppa constant velocity joint of claim 1, wherein: e1= e2= (0.20-0.27) d0, and d0 is the diameter of the steel ball.
3. The wide angle high efficiency eight steel ball rzeppa constant velocity joint according to claim 1 or 2, wherein: and when the angle of the universal joint is 0 degree, the distance between the centers of the two steel balls in each pair of rolling paths is the steel ball center diameter d1, d1= (3.9-4.3) d 0.
4. The high angle, high efficiency eight steel ball rzeppa constant velocity joint of claim 3, wherein: the L1/L2/L3= (0.20-0.27) d 0.
5. The high angle, high efficiency eight steel ball rzeppa constant velocity joint of claim 4, wherein: the radiuses R1= (1.65-1.85) × d0 of the outer circular arc II and the inner circular arc III of the first pair of inner and outer raceways; the radiuses R2= (0.85-1.0) × d0 of the outer circular arc II and the inner circular arc III of the third pair of inner and outer raceways; and the radiuses R3= (1.5-1.7) × d0 of the outer circular arc II and the inner circular arc III of the second inner raceway and the fourth outer raceway.
6. The high angle, high efficiency eight steel ball rzeppa constant velocity joint of claim 5, wherein: the outer diameter D = (5.6-6.0) × D0 of the outer bell housing.
7. The high angle, high efficiency eight steel ball, rzeppa constant velocity joint of claim 6, wherein: the star-shaped sleeve is connected with the driving shaft through an involute spline and adopts a full-through type middle snap ring positioning structure or an end snap ring positioning structure with a positioning table; the outer end of the outer shell is provided with a thread with a locking function.
8. The wide angle high efficiency eight steel ball rzeppa constant velocity joint according to claim 1 or 2, wherein: the L1/L2/L3= (0.20-0.27) d 0.
9. The wide angle high efficiency eight steel ball rzeppa constant velocity joint according to claim 1 or 2, wherein: the radiuses R1= (1.65-1.85) × d0 of the outer circular arc II and the inner circular arc III of the first pair of inner and outer raceways; the radiuses R2= (0.85-1.0) × d0 of the outer circular arc II and the inner circular arc III of the third pair of inner and outer raceways; and the radiuses R3= (1.5-1.7) × d0 of the outer circular arc II and the inner circular arc III of the second and fourth pairs of raceways.
10. The wide angle high efficiency eight steel ball rzeppa constant velocity joint according to claim 1 or 2, wherein: the star-shaped sleeve is connected with the driving shaft through an involute spline and adopts a full-through type middle snap ring positioning structure or an end snap ring positioning structure with a positioning table; the outer end of the outer shell is provided with a thread with a locking function.
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| CN112211915A (en) * | 2020-09-28 | 2021-01-12 | 万向钱潮股份有限公司 | Efficient rzeppa constant velocity universal joint |
| CN113623335A (en) * | 2021-08-23 | 2021-11-09 | 万向钱潮股份有限公司 | High-efficiency long-life fixed end ball cage type constant velocity universal joint |
| CN113775664A (en) * | 2021-09-26 | 2021-12-10 | 上海纳铁福传动系统有限公司 | Ball cage type constant velocity universal joint |
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