CN216430321U

CN216430321U - Wide-angle multi-steel ball rzeppa constant velocity universal joint

Info

Publication number: CN216430321U
Application number: CN202122952347.4U
Authority: CN
Inventors: 张杰飞; 李月; 郭宇; 张静龙; 何凯; 王会利; 姚东
Original assignee: Nexteer Lingyun Driveline Zhuozhou Co Ltd
Current assignee: Nexteer Lingyun Driveline Zhuozhou Co Ltd
Priority date: 2021-11-29
Filing date: 2021-11-29
Publication date: 2022-05-03
Anticipated expiration: 2031-11-29

Abstract

The utility model discloses a large-angle multi-steel ball rzeppa constant velocity universal joint, wherein the center line of the inner spherical surface where the inner cavity of a bell-shaped shell is positioned is superposed with the center line of the outer spherical surface where the outer surface of a star-shaped sleeve is positioned; in the state of 0 angle of the universal joint, the track of the center of the steel ball is a single-section circular arc A when the steel ball rolls along the inner raceway of the bell-shaped shell, and the track of the center of the steel ball is a single-section circular arc B when the steel ball rolls along the outer raceway of the star-shaped sleeve; the centers of the circular arcs A and B are on the axis of the universal joint; the eccentricity between the center line of the circular arc A and the center line of the inner/outer spherical surface is E1; the eccentricity between the center line of the circular arc B and the center line of the inner/outer spherical surface is E2; e2= D3/2 TAN (12-19), E1= (1.3-2.2) E2. The utility model discloses a biggest bell shell envelope external diameter is less relatively, and on axostylus axostyle diameter does not reduce, quiet turn round and fatigue strength does not reduce, universal joint durability keeps unchangeable or further the basis that improves, the biggest angle can reach 52 angles bigger even.

Description

Wide-angle multi-steel-ball rzeppa constant velocity universal joint

Technical Field

The invention belongs to the field of automobile parts and relates to a large-angle multi-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. 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 universal joint needs to adopt a compression design as much as possible, the envelope size is small, the strength and the durability are high, and meanwhile, the universal joint needs to have the characteristic of high efficiency to avoid power loss; also, the turning radius of the vehicle is required to be as small as possible to facilitate the turning of the vehicle, which requires a higher maximum angle of the universal joint.

The conventional birfield constant velocity joint includes: the RZ type and the UF type have a maximum angle of only 47 ° and a maximum angle of only 50 ° and cannot reach 52 °. For the novel ball cage type constant velocity universal joint disclosed in the literature, the maximum universal joint angle can reach 52 degrees, but the track of the universal joint is S-shaped or formed by multiple arcs and straight lines, a larger maximum enveloping outer diameter of an outer bell shell is needed, the weight is heavier, the track of a raceway is complex, the processing can be carried out unless special multi-axis processing hard milling equipment is provided, a common imported grinding machine is adopted, the processing and manufacturing of the complex track of the raceway cannot be finished, the processing cost and the detection cost are high, and the further lightweight development of an automobile is limited. In addition, no matter how the track shape of the ball cage type constant velocity universal joint changes, the offset distance between the ball track and the spherical surface of the outer race and the inner race is always basically equal or has extremely small difference, and the maximum difference can only reach 0.1 mm.

SUMMERY OF THE UTILITY MODEL

The utility model aims at solving the above-mentioned problem that exists among the prior art, a many steel balls of wide-angle rzeppa constant velocity universal joint is provided, the biggest bell shell envelope external diameter of this universal joint is compared with other types universal joints of specification and is smaller, on axostylus axostyle diameter does not reduce, quiet turn round and fatigue strength does not reduce, universal joint durability keeps unchangeable or further improves the basis, the biggest angle can reach 52 and more angle even, the orbit is simple, the shape is simple, and the processing of being convenient for, the cost is relatively lower.

In order to achieve the above object, the technical solution of the present invention is: a large-angle multi-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 n steel balls, wherein n =6,7,8,9 and 10; n steel balls which are kept in a plane by annular retainers with n windows uniformly distributed at intervals are arranged between the roller path of the star-shaped sleeve and the roller path of the outer shell, and the two roller paths are in transition fit with the steel balls; the inner wall of the bell-shaped shell and the outer 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 small clearance fit; 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; the surface of the inner cavity of the outer shell is provided with n identical inner raceways, and the outer surface of the inner sleeve is provided with n identical outer raceways at the positions corresponding to the inner raceways; the track of the center of the steel ball is a single-section arc A when the steel ball rolls along the inner raceway of the outer race of the star-shaped sleeve, and the track of the center of the steel ball is a single-section arc B when the steel ball rolls along the outer raceway of the star-shaped sleeve; under the state of the angle of the universal joint 0, the centers of the circular arc A and the circular arc B are on the axis of the universal joint; the center line of the circular arc A is positioned on the side of the shaft rod of the universal joint, and the eccentricity between the center line of the circular arc A and the center line of the inner/outer spherical surface is E1; the center line of the circular arc B is positioned at the side of the bell-shaped shell opening, and the eccentricity between the center line of the circular arc B and the center line of the inner/outer spherical surface is E2; the diameter D of each steel ball and the diameter D3 of a circle where the center of each steel ball is located are known values, the offset distance E2= D3/2 TAN (12-19) of the outer race of the star sleeve, and the offset distance E1= (1.3-2.2) = E2 of the inner race of the outer race.

More preferably, the outer spherical surface diameter D5= D3+ (7-9) and the inner spherical surface diameter D6= D3- (3-7).

Further preferably, the diameter of the joint of the outer shell and the dust cover is D2= D3+ D + (20-32).

Further preferably, the maximum outer diameter of the outer bell housing is D1= D2+ (0-0.5).

The utility model discloses a carry out special proportional design through the offset distance to bell shell and star cover, form great difference and realize that the universal joint is not reducing quiet turning round, quiet turning round and fatigue strength like, do not reduce the wearability, do not reduce the durability and improved the durability even, envelope size is not increased or even the biggest bell shell envelope external diameter compares other types universal joint of same specification less, the axostylus axostyle diameter is on the basis that does not reduce, through the great difference offset of setting for bell shell and star cover, and then shorten the axial displacement of steel ball on the bell shell track and realize the function of the large angle of universal joint, the biggest angle can reach 52 angles even more. The track of the center of the steel ball when the steel ball rolls along the inner raceway of the outer race of the inner race of the outer race of the inner race and the track of the center of the steel ball when the steel ball rolls along the outer raceway of the inner race of the outer race are both single-section arcs, and the steel ball rolling device is simple in track, simple in shape, convenient to process, lower in processing cost and lower in detection cost.

Drawings

Fig. 1 is a schematic view of the internal structure of the present invention at an angle of 0 °;

fig. 2 is a schematic view of the internal structure of the present invention at an angle of 52 °;

FIG. 3 is a front cross-sectional view of the middle bell housing of the present invention;

FIG. 4 is a front cross-sectional view of the inner race of the present invention;

FIG. 5 is a left side view of the middle star-shaped sleeve of the present invention;

fig. 6 is a front sectional view of the holder of the present invention;

fig. 7 is a right side view of the middle retainer of the present invention.

Detailed Description

The present invention will be further described with reference to the following embodiments.

As shown in fig. 1 to 7, the present embodiment includes an outer race 2 provided with an inner cavity, an inner race 1 located in the inner cavity of the outer race 2, an annular cage 3, and 8 (6, 7, 9, or 10) steel balls 4. 8 steel balls 4 which are kept in one plane by an annular retainer 3 with 8 (6, 7, 9 or 10) windows 9 uniformly distributed at intervals are arranged between the raceway of the star-shaped sleeve 1 and the raceway of the outer shell 2, and the two raceways are in transition fit with the steel balls 4. The inner wall of the outer shell 2 and the outer wall of the annular retainer 3 form a group of spherical pairs, the inner wall of the annular retainer 3 and the outer wall of the star-shaped sleeve 1 form another group of spherical pairs, and the two groups of spherical pairs are in small clearance fit. The spherical surface of the inner cavity of the outer shell 2 is an inner spherical surface, the spherical surface of the outer surface of the inner sleeve 1 is an outer spherical surface, and the central line 6 of the inner spherical surface is superposed with the central line 7 of the outer spherical surface. The surface of the inner cavity of the outer shell 2 is provided with 8 identical inner raceways 11, and the outer surface of the inner race 1 is provided with 8 identical outer raceways 10 at the positions corresponding to the inner raceways. The track of the center of the steel ball is a single-section arc A when the steel ball 4 rolls along the inner raceway 11 of the outer race 2, and the track of the center of the steel ball is a single-section arc B when the steel ball 4 rolls along the outer raceway 10 of the inner race 1. In the 0 ° angle state of the joint, the centers of arc a and arc B are both on the joint axis 12. The center line 8 of the circular arc A is positioned on the side of the shaft rod of the universal joint, and the eccentricity between the center line of the circular arc A and the center line of the inner/outer spherical surface is E1; the center line 5 of the circular arc B is located on the bell housing mouth side, and the eccentricity from the center line of the inner/outer spherical surface is E2. The diameter D of each steel ball is a given value, the diameter D3 of a circle where the center of each steel ball is located is set according to D and universal joint wear performance evaluation, and is also a known value, and the offset distance E2= D3/2 TAN (12-19) of the outer raceway of the star sleeve 1 and the offset distance E1= (1.3-2.2) E2 of the inner raceway of the outer race 2.

The offset distance E1 of the outer shell 2 and the offset distance E2 of the inner race 1 are not equal, and E1= (1.3-2.2) × E2. The following example is used to schematically analyze the relationship between the angle of deflection of the cage 3 and the angle of the gimbal, and it is assumed that the gimbal angle is 52 °, the offset distance E1=6.9518, the offset distance E2=4.3449, which is 1.6 times, and the offset distances are greatly different from each other, see fig. 2.

A is the center of the race track of the inner race, B is the center of the race track of the outer race, and O is the center of the circle in which the centers of the steel balls are located. In triangular AOB, angle AOB = 180-52 ° =128 °.

By using the cosine theorem, AB = SQRT (E1^2+ E2^2-2 ^ E1^ E2^ COS (128)) =10.218,

by adopting sine theorem, the angle ABO = ASIN (E2/(E1/SIN (128 °)) =19.578 °,

the deflection angle of the cage is ═ O1OO 1' =19.578 °, namely the angle of rotation of the cage.

Therefore, when the angle of the universal joint is 52 degrees, the deflection angle of the retainer is 19.578 degrees, which is smaller than the deflection angle of the conventional universal joint retainer, so that the axial projection length of the stroke of the steel ball on the roller way in the outer shell is relatively smaller, the stroke requirement is met, and the large angle of the universal joint is realized. Meanwhile, the maximum outer diameter of the outer envelope of the outer bell-shaped shell of the universal joint is smaller than that of other universal joints of the same specification.

Preferably, the diameter of the outer spherical surface of the retainer 3 is D5= D3+ (7-9); the diameter D6= D3- (3-7) of the inner spherical surface of the retainer 3.

Preferably, the diameter of the joint between the outer shell 2 and the dust cover is D2= D3+ D + (20-32).

Preferably, the maximum outer diameter D1= D2+ (0-0.5) of the outer shell 2.

Isokinetic analysis:

o1'A' and O1'B' are from FIG. 1, O1A and O1B are from FIG. 2, and represent the segment between characteristic points of the gimbal at 0 degree and a specific angle, respectively, O1A = O1'A' = SQRT ((D3/2) ^2-E2^2), and O1B = O1'B' = SQRT ((D3/2) ^2-E1^ 2).

For a universal joint with given parameters, the values of O1A and O1B line segments are constant, namely represent the distance from the center of a steel ball to the center of a race of an inner race of a star sleeve and the distance from the center of the steel ball to the center of a race of an outer race respectively under the state of the universal joint, under the angle of the universal joint of 0 degree, the centers of the two races are on the longitudinal axis of the universal joint, the track of the races is a single circular arc, and the center of the circle has no radial offset;

since E1< E2 and thus O1A < O1B, the two are not very different, as exemplified by the exemplary dimensions of figure 2,

O1A =34.208, O1B =34.265, with a difference of 0.057.

At any angle, the ball rolls and slides between the inner and outer races, with a constant linear velocity V for the inner and outer races, an angular velocity ω different with respect to the inner and outer races due to the difference in radii O1A and O1B, an angular velocity ω 1 for the outer race of the inner race of the spider connected to the shaft, an angular velocity ω 1 for the inner race of the bell housing, an angular velocity ω 2, ω 1> ω 2, but with a small difference, ω 2= (34.208/34.265) × ω 1=0.99834 ω 1, as an example.

That is, the rotational speed transmitted from the transmission end is transmitted to the wheel end joint and the wheels, the rotational speed is reduced extremely slightly, but the angular speeds of the parts inner race and outer race representing the input and output are respectively kept constant during the rotation and running of the joint, and the specific value difference is extremely small, namely, the constant velocity is kept constant, and the joint of the design is still a pure constant velocity joint.

Wedge angle self-locking description:

in fig. 1, the joint wedge angle is δ =2 ∈, and taking the example of fig. 2 as an example, the wedge angle is 18.9 ° when the joint angle is 0 °; when the angle of the universal joint is 52 degrees, the wedge angle is 17.1 degrees, and the universal joint cannot generate self-locking under the angle.

Static torsion-like strength description:

according to the size setting, the static torsion-like strength can reach the strength of a covering constant velocity universal joint with the same specification in the range of 0-52 degrees of the universal joint (the static torsion-like strength is large because the rotating angle of the retainer is small, and the retainer is supported by the outer shell to be large under the condition of a large universal joint angle.

Durability/wear description:

according to the size setting to and the application of many steel balls of possibility, at the universal joint 0 to 52 within ranges, the utility model discloses the wearing and tearing performance that corresponds the design is higher than the 6 balls of equal specification and hides clap formula constant velocity universal joint (because of many balls are used and holder deflection angle is little).

Description of the strength:

according to the size setting, the diameter of the shaft rod is not reduced in the range of 0-52 degrees of the universal joint, and the static torsion and the fatigue strength can meet the same requirements of the covering type constant velocity universal joint.

The above-described embodiments are merely preferred and exemplary and are not intended to limit the present invention, and any modification, equivalent replacement, or improvement made without departing from the spirit and principle of the present invention shall fall within the protection scope of the present invention.

Claims

1. A big-angle multi-steel-ball rzeppa constant velocity universal joint is characterized in that: the steel ball bearing comprises an outer bell shell with an inner cavity, a star-shaped sleeve positioned in the inner cavity of the outer bell shell, an annular retainer and n steel balls, wherein n =6,7,8,9 and 10; n steel balls which are kept in a plane by an annular retainer with n windows uniformly distributed at intervals are arranged between the roller path of the star-shaped sleeve and the roller path of the outer shell, and the two roller paths are in transition fit with the steel balls; the inner wall of the bell-shaped shell and the outer 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 small clearance fit; 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; the surface of the inner cavity of the outer shell is provided with n identical inner raceways, and the outer surface of the inner sleeve is provided with n identical outer raceways at the positions corresponding to the inner raceways; the track of the center of the steel ball is a single-section arc A when the steel ball rolls along the inner raceway of the outer race of the star-shaped sleeve, and the track of the center of the steel ball is a single-section arc B when the steel ball rolls along the outer raceway of the star-shaped sleeve; under the state of the angle of the universal joint 0, the centers of the circular arc A and the circular arc B are on the axis of the universal joint; the center line of the circular arc A is positioned on the side of the shaft rod of the universal joint, and the eccentricity between the center line of the circular arc A and the center line of the inner/outer spherical surface is E1; the center line of the circular arc B is positioned at the side of the bell-shaped shell opening, and the eccentricity between the center line of the circular arc B and the center line of the inner/outer spherical surface is E2; the diameter D of each steel ball and the diameter D3 of a circle where the center of each steel ball is located are known values, the offset distance E2= D3/2 TAN (12-19) of the outer race of the star sleeve, and the offset distance E1= (1.3-2.2) = E2 of the inner race of the outer race.

2. The high angle multi-ball birfield constant velocity joint of claim 1, wherein: the diameter D5= D3+ (7-9) of the outer spherical surface of the retainer, and the diameter D6= D3- (3-7) of the inner spherical surface.

3. A high angle multi-ball birfield constant velocity joint as claimed in claim 1 or 2, wherein: the diameter D2= D3+ D + (20-32) of the joint of the outer shell and the dust cover.

4. A high angle multi-ball birfield constant velocity joint as claimed in claim 3, wherein: the maximum outer diameter D1= D2+ (0-0.5) of the outer shell.

5. A high angle multi-ball birfield constant velocity joint as claimed in claim 1 or 2, wherein: the maximum outer diameter D1= D2+ (0-0.5) of the outer shell.