KR20150015324A - Fixed type constant velocity joint - Google Patents

Fixed type constant velocity joint Download PDF

Info

Publication number
KR20150015324A
KR20150015324A KR1020130091258A KR20130091258A KR20150015324A KR 20150015324 A KR20150015324 A KR 20150015324A KR 1020130091258 A KR1020130091258 A KR 1020130091258A KR 20130091258 A KR20130091258 A KR 20130091258A KR 20150015324 A KR20150015324 A KR 20150015324A
Authority
KR
South Korea
Prior art keywords
track
outer ring
joint
inner ring
cage
Prior art date
Application number
KR1020130091258A
Other languages
Korean (ko)
Inventor
김필기
Original Assignee
현대위아 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 현대위아 주식회사 filed Critical 현대위아 주식회사
Priority to KR1020130091258A priority Critical patent/KR20150015324A/en
Publication of KR20150015324A publication Critical patent/KR20150015324A/en

Links

Images

Classifications

    • 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
    • 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
    • F16D3/2237—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 where the grooves are composed of radii and adjoining straight lines, i.e. undercut free [UF] type joints
    • 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

Abstract

The present invention relates to a fixed ball-type constant velocity joint capable of improving durability life, improving strength of a cage, and improving torque transmission efficiency,
An inner ring rotatably receiving an engine-side rotational power and having an outer race track formed on an inner surface thereof; And a cage formed with a window for supporting the two balls, wherein each of the outer ring tracks formed on the inner surface of the outer ring has one pair of two outer rings, And the inner ring tracks formed on the outer surface of the inner ring are formed as one pair and correspond to the outer ring tracks of the outer ring, And the pair of inner ring tracks are inclined by a skew angle in the opposite directions with respect to the joint axis line X. [

Description

Fixed type constant velocity joint "

The present invention relates to a fixed ball-type constant velocity joint, more specifically, to a fixed ball-type constant velocity joint capable of improving durability life, improving strength of a cage, and improving torque transmission efficiency.

Generally, a joint is for transmitting rotational power (torque) to a rotation shaft having different angles of rotation axis. In the case of a propulsion shaft having a small power transmission angle, a hook joint, a flexible joint or the like is used. A constant velocity joint is used.

Since the constant velocity joint can transmit power smoothly at a constant speed even when the angle of intersection between the drive shaft and the driven shaft is large, it is mainly used for the axle shaft of the independent suspension type front wheel drive vehicle, and the transmission side (inboard side) It is composed of a tripod type constant velocity joint or a slide type ball type constant velocity joint. The wheel side (outboard side) is composed of a constant ball type constant velocity joint around the shaft.

The tripod type constant velocity joint on the transmission side and the slide type ball type constant velocity joint absorb the displacement of the vehicle through the axial movement and the folding motion, and the fixed ball type constant velocity joint of the wheel side rotates by the steering angle of the wheel, do.

The fixed ball type constant velocity joint described above is divided into a ball joint having a maximum angle of 47 degrees and a track of the outer and inner rings formed by a curved line and a straight line and an undercut ball joint having a maximum angle of 50 degrees.

FIG. 1 is a perspective view of a fixed undercut ball joint of a general vehicle, FIG. 2 is a front view of a fixed undercut ball joint of a general vehicle, and FIG. 3 is a sectional view taken along line H-H of FIG.

As shown in Figs. 1 to 3, a general structure of a slide type ball type joint of a vehicle includes an outer ring 5 having an outer ring track 51 formed on an inner surface thereof, An inner ring 6 provided inside the outer ring 5 and having an inner ring track 61 formed on its outer surface and a plurality of balls 6 for transmitting the rotational power of the outer ring 5 to the inner ring 6, (8), and a cage (7) for supporting the ball (8).

The above-mentioned outer ring track 51 is formed in the longitudinal direction of the HH end face in the X axis direction. The inner ring track 61 is also formed in the longitudinal direction of the HH end face X axis. Respectively, in the radial direction.

The outer ring track 51 is composed of a curved track 51-1 and a straight track 51-2 and the center O1 'of the track radius R51 of the curved track 51-1 is located on the center axis Is offset by f 'on the X-axis. The center of the inner spherical surface 52 of the outer ring 5 is the joint rotation center O and rotates in contact with the outer spherical surface 71 of the cage 7. [

The inner ring track 61 is composed of a curved track 61-1 and a straight track 61-2 and the center O2 'of the track radius R61 of the curved track 61-1 is a center axis And is positioned symmetrically with the center O1 'of the track radius R51 of the outer ring 5 with the joint rotation center O' therebetween. The center of the outer spherical surface 62 of the inner ring 6 is the joint rotation center O 'and is in contact with the inner spherical surface 72 of the cage 7 and rotates.

The center of the outer spherical surface 71 and the inner spherical surface 72 of the cage 7 is defined by the center of the joint rotation center O ' Restrained on board. The cage 7 and the ball 8 on the inner ring 6 are positioned on one plane and are rotated by a half angle of the angle of the inner ring 6.

The action of a fixed undercut ball joint of a general vehicle according to the above configuration is as follows.

When a rotational power output from an engine (not shown) is transmitted to the outer ring 5 via a transmission (not shown), rotational power is transmitted to the inner ring 6 through the ball 8, .

The ball 8 is restrained by the window 73 of the cage 7 and the ball 8 is held between the track 51 of the outer ring 5 and the track 61 of the inner ring 6 And transmits the torque in the rotational direction.

The inner spherical surface 52 of the outer ring 5 restrains the outer spherical surface 71 of the cage 7 and the inner spherical surface 72 of the cage 7 restrains the outer spherical surface 62 of the inner race 6, And the window 73 of the cage 7 restrains the ball 8 so that axial sliding and folding motion are caused so that the ball 8 slides on the track 51 of the outer race 5 It is folded according to the displacement of the vehicle.

3, the contact force Fo between the ball 8 and the outer ring track 51 of the outer ring 5 and the contact force Fo between the ball 8 and the inner ring track 61 of the inner ring 6 The contact force Fi causes the ball 8 to come into contact with the window 73 of the cage 7 and generate an axial force Fc to push the cage 7 in the direction of the outer ring entrance. The axial force Fc is generated in the same direction toward the inlet side of the outer ring of the eight balls irrespective of the reduction state or the ball phase.

However, in the conventional fixed undercut ball joint as described above, in the curved track 51-1 of the outer ring 5, the depth of the outer ring entrance track groove depth 5a 'and the depth of the outer ring inner track groove depth 5b' The contact area between the ball 8 and the curved track 51-1 of the outer ring 5 is reduced and the contact stress is increased so that the curved track 51-1 of the ball 8 and the outer ring 5 ) Contact stress is increased and the durability life is reduced.

In order to secure a proper contact stress between the ball 8 and the curved track 51-1 of the outer ring 5, the outer diameter of the outer ring 5 must be increased, which leads to a problem of increased size of the component.

In the conventional fixed undercut ball joint, the center O1 'of the track radius R51 of the outer ring 5 and the center O2' of the track radius R61 of the inner ring 6 are symmetrical on the X- the contact force Fo between the ball 8 and the track 51 of the outer ring 5 and the contact force Fi between the ball 8 and the inner ring 6 of the track 61 The ball 8 is brought into contact with the window 73 of the cage 7 to generate an axial component force Fc which pushes the cage 7 in the direction of the outer ring entrance, There is a problem that the strength of the cage 7 is lowered by generating eight balls in the same direction on the outer ring inlet side regardless of the ball phase.

If the offset amount f 'is reduced for the reduction of the axial component Fc, the component force acting on the ball 8 is reduced by a factor < RTI ID = 0.0 > There is a problem in that when the ball 8 becomes small and the ball 8 is in a no-load state, the ball 8 is caught or the operation becomes difficult.

SUMMARY OF THE INVENTION An object of the present invention is to provide a fixed ball-type constant velocity joint capable of improving durability, improving strength of a cage, and improving torque transmission efficiency, .

According to a first aspect of the present invention, there is provided an internal combustion engine comprising: an outer ring rotatably receiving an engine-side rotational power and having an inner race track formed on an inner surface thereof; A plurality of balls for transmitting the rotational power of the outer ring to the inner ring and a cage having a window for supporting the balls in two at a time, And the pair of outer ring tracks are inclined by a skew angle? In opposite directions with respect to the joint axis line X. The outer ring tracks formed on the outer surface of the inner ring are divided into two by two And the pair of inner ring tracks are inclined by a skew angle in opposite directions with respect to the joint axis X, Preferable.

The configuration of the present invention is such that the outer ring track is divided into a tapered track having a curved track and a tapered angle, and the two tracks are preferably in contact with each other.

In the structure of the present invention, the inner ring track is divided into a tapered track having a curved track and a tapered angle, and the two tracks are preferably in contact with each other.

In the configuration of the present invention, the track radius center of the curved track of the above-mentioned outer ring track is offset vertically from the joint rotation center O by f, and the center of the inner ring diameter is defined as the outer radius of the cage Contact.

In the configuration of the present invention, the center of the track radius of the curved track of the above-described inner ring track is offset vertically from the joint rotation center (O) by f, and the center of the bore in the outer ring is centered on the outer radius of the cage Contact.

The configuration of the present invention is preferably such that the ratio of the outside cage width to the end window width (the outside window width / the end window width is 0.85 to 0.95).

The constitution of this invention is preferable if it is applied to a joint having eight or more balls.

According to the present invention, the durability life is improved, the strength of the cage is improved, and the torque transmission efficiency is improved.

1 is a perspective view of a fixed undercut ball joint of a general vehicle.
2 is a front view of a fixed undercut ball joint of a general vehicle.
3 is a sectional view taken along the line HH in Fig.
4 is a front view of a fixed ball-type constant velocity joint according to an embodiment of the present invention.
5 is a sectional view taken along line AA in Fig.
6 is a sectional view taken along line BB of Fig.
7 is a cross-sectional view taken along line C1-C1 and line C2-C2 in Fig.
8 and 9 are views for explaining the skew angle of an inner ring track of a fixed ball-type constant velocity joint according to an embodiment of the present invention.
10 is a sectional view taken along line DD of Fig.
Fig. 11 is a sectional view taken along line EE of Fig. 8 and Fig.
12 is a perspective view of an outer ring of a fixed ball-type constant velocity joint according to an embodiment of the present invention.
13 is a perspective view of an inner ring of a fixed ball-type constant velocity joint according to an embodiment of the present invention.
FIG. 14 is a cross-sectional structural view showing a fixed ball-type constant velocity joint according to an embodiment of the present invention implemented in an 8-ball type.
15 is a graph comparing the axial ball components of a fixed ball-type constant velocity joint according to an embodiment of the present invention.
16 is a graph comparing the contact stresses of a fixed ball-type constant velocity joint according to an embodiment of the present invention.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings, so that those skilled in the art can easily carry out the present invention. Other objects, features, and operational advantages, including the purpose, operation, and effect of the present invention will become more apparent from the description of the preferred embodiments.

It is to be understood that both the foregoing general description and the following detailed description of the present invention are exemplary and explanatory only and are not to be construed as limiting the scope of the invention as disclosed in the accompanying claims. It is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, is intended to cover various modifications and similarities, many of which are within the scope of the present invention.

Also, terms and words used in the description and claims of the present invention are defined based on the principle that the inventor can properly define the concept of a term in order to explain its invention in the best way, And should not be construed as limited to only the prior art, and should be construed in a meaning and concept consistent with the technical idea of the present invention. For example, the terms relating to directions are set on the basis of the position represented on the drawing for convenience of explanation.

As shown in Figs. 4 to 13, the configuration of the fixed ball-type constant velocity joint according to the embodiment of the present invention is characterized in that the outer race tracks 11a, 11b, 11c (21a, 21b, 21c, 21d, 21e) provided on the outer surface of the outer ring (1) A plurality of balls 41, 42, 43 and 44 for transmitting the rotational power of the outer ring 1 to the inner ring 2; And a window for supporting the balls 41, 42, 43, 44, 45, 46, 47, 48, 49, (7).

The outer ring tracks 11a, 11b, 11c, 11d, 11e, 11f, 11g, 11h, 11i and 11j formed on the inner surface 12 of the outer ring 1 are formed into five pairs And is configured to be inclined by a skew angle? In opposite directions with respect to the joint axis line X as shown in the example of the pair of outer ring tracks 11a and 11b shown in FIG.

The inner wheel tracks 21a, 21b, 21c, 21d, 21e, 21f, 21g, 21h, 21i, and 21j formed on the outer surface 22 of the inner ring 2 are formed as two pairs, And corresponds to the five pairs of outer ring tracks of the outer ring 1 with the balls 41, 42, 43, 44, 45, 46, 47, 48, 49 and 40 interposed therebetween.

The inner wheel tracks 21a, 21b, 21c, 21d, 21e, 21f, 21g, 21h, 21i, and 21j formed on the outer surface 22 of the inner ring 2 described above, As shown in the example of the inner ring track 21b shown in Fig. 9 and the inner ring track 21b shown in Fig. 9, the skew angle?

Therefore, if the inner ring track 21a has a positive skew angle + alpha inclined to the right with respect to the joint axis X, the outer ring track 11a corresponding to the ball 41 is inclined to the left with the ball 41 interposed therebetween And has a true minus skew angle (-α). When the inner ring track 21b has a minus skew angle -α that is inclined to the left with respect to the joint axis X, the outer ring track 11b corresponding to the ball 42 is inclined to the right with the ball 42 therebetween And a positive plus skew angle (+ alpha).

10 is a sectional view taken along the line D-D in Fig. 7, showing a taper angle? And a vertical offset shape applied to the outer ring track 11. As shown in Fig.

As shown in Fig. 10, the outer ring track 11 is divided into a curved track 11-1 and a tapered track 11-2 having a taper angle?, And the two tracks are in contact with each other. The center O1 of the track radius R11 of the curved track 11-1 is offset vertically f from the joint rotation center O and the center of the inner ring diameter 12 is located at the joint rotation center O And comes into contact with the outer radius (31) of the cage (3).

Fig. 11 is a sectional view taken along line E-E of Fig. 8 and Fig. 9, showing a taper angle? And a vertical offset shape applied to the inner ring track 21. Fig.

As shown in Fig. 11, the inner ring track 21 is divided into a curved track 21-1 and a tapered track 21-2 having a taper angle?, And the two tracks are in contact with each other. The center O1 of the track radius R21 of the curved track 21-1 is offset vertically f from the joint rotation center O and the center of the inner ring outer diameter 22 is centered on the joint rotation center O And comes into contact with the end radius (32) of the cage (3).

The cage 3 has the outer ring 1 and the inner ring 2 so that the outer surface 31 faces the inner surface 12 of the outer ring 1 and the inner surface 32 faces the outer surface 22 of the inner ring 2. [ Are assembled between the inner ring 2 and a pair of balls are housed in each of the five cage windows to constrain the balls so that the center of the ball is always located on one plane.

The ratio of the outside opening width 35 to the end opening width 35 of the cage 3 outside the cage 3 is about 0.85 to 0.95 so that interference with the ball is avoided, It is possible to secure a large area of the column Ca.

The balls 41, 42, 43, 44, 45, 46, 47, 48, 49 and 40 are located at the intersections of the Y1 and Y2 axes passing through the joint rotation center O and the PCD, (111) and the inner ring track (211).

FIG. 14 is a cross-sectional structural view showing a fixed ball-type constant velocity joint according to an embodiment of the present invention implemented in an 8-ball type.

As shown in FIG. 14, the fixed ball type constant velocity joint according to the embodiment of the present invention is configured such that the outer race tracks 11a ', 11b', 11c ' 21d ', 21e', 11e ', 11e', 11e ', 11f', 11g ', 11h' are formed on the outer surface of the outer ring, A plurality of balls 41 ', 42', 43 ', 44', 45 ', 46', and 45 'for transmitting the rotational power of the outer ring to the inner ring, 47 ', 48', and a window for supporting the balls 41 ', 42', 43 ', 44', 45 ', 46', 47 ', 48' And the skew angle alpha, the taper angle beta and the vertical offset f are applied in the same manner.

The operation of the fixed ball-type constant velocity joint according to the embodiment of the present invention with the above-described structure is as follows.

When the rotational power output from the engine is transmitted to the outer ring 1 through the transmission, rotational power is transmitted to the inner ring 2 through the plurality of balls to rotate the wheel (not shown).

In this case, the outer ring track 11 and the inner ring track 21 are arranged so that the skew angle? Crosses in the + and - directions, and the taper angle? And the vertical offset are applied, The joint force of the joint is given by the taper angle?, And the durability life can be improved by the vertical offset f. This will be explained in more detail.

1. Role of skew angle (α)

7 to 9, the contact force Fo1 generated between the ball 41 of the Y1 axis and the outer ring track 11a and the contact force Fi1 generated between the ball 41 of the Y1 axis and the inner ring track 21a The ball 41 generates a force Fc1 pushing the cage window 33. [ The direction of the component Fc2 is opposite to the component Yc of the Y1 axis because the skew angle alpha of the outer ring track 11b and the inner ring track 21b is opposite to the Y1 axis in the case of the adjacent Y2- (Fc1, Fc2) which are opposite in direction are placed in one cage window (33), thereby imparting operability to each ball and canceling each other's forces in the same cage opening Which helps to improve the strength of the cage. The two components Fc1 and Fc2 are located in pairs in the radial direction.

As described above, by applying the skew angle?, The axial component force Fc1 of the cage Y1 axis and the axial component force Fc2 of the Y2 axis are inversely canceled each other and the taper angular axial force Fz, And the cage strength can be improved. As the cage strength is improved, the volume of the cage window column (Ca) can be reduced, so that it is possible to apply balls having 10 or more balls.

FIG. 15 is a graph comparing axial ball components of a fixed ball-type constant velocity joint according to an embodiment of the present invention. The axial component Fc1 of the cage Y1 axis and the axial component Fc2 of the Y2 axis When the taper angular component force Fz is generated to cancel the directions opposite to each other and to give operability, the frictional resistance between the components is reduced due to the reduction of the axial component force, thereby improving the torque transmission efficiency.

2. Role of taper angle (β)

The tapered track having the taper angle beta generates a contact force Fto between the ball and the outer ring track 11 and generates a contact force Fti between the ball 4 and the inner ring track 21, Directional component Fz. The axial component force Fz serves to impart the operability of the joint.

The skew angle alpha of the outer ring track 11 and the skew angle alpha of the inner ring track 21 coincide with each other according to the phase of the ball when the angle is reduced by 2 alpha which is twice the skew angle alpha. When the axial force Fc is canceled by the coincidence of the contact force Fo generated between the outer ring track 11 and the outer ring track 11 and the contact force Fi generated between the ball and the inner ring track 21, And is caught in the track. To prevent this, a tapered track is used to generate a constant axial component force (Fz) at any phase to impart operability to the ball.

The axial ball component Fc by the skew angle alpha is proportional to the magnitude of the skew angle alpha and the axial ball component Fz by the taper angle beta is proportional to the taper angle beta It is proportional.

3. Role of vertical offset (f)

As shown in Fig. 10, the vertical offset f increases the outer-radius curved track radius R11 to maintain the outer-wheel curved track 11-1 groove depth at the same level. It can be confirmed that the track groove depth 5a at the time of low-angle-of-use and the track groove depth 5b at the time of high-angle play are the same. This serves to increase durability not only at low angles but also at resting angles.

Conventionally, as the angle increases, the depth of the track groove of the outer race becomes shallower, the durability life is lowered, and the strength is lowered at the time of hardening. However, according to the present invention, when the vertical offset f is applied, the track radius of the outer ring is increased and the track groove depth 5a at the low angle and the track groove depth 5b at the time of the high angle are kept constant, thereby increasing the durability life and improving the strength Can be obtained.

FIG. 16 is a graph comparing the contact stresses of a fixed ball-type constant velocity joint according to an embodiment of the present invention. In the prior art, as the angle increases, the contact stress increases. On the other hand, .

1: outer ring 2: inner ring
3: Cage

Claims (7)

An outer ring rotatably receiving an engine-side rotational power and having an outer race track formed on an inner surface thereof,
An inner ring disposed inside the outer ring and having an inner ring track formed on an outer surface thereof,
A plurality of balls for transmitting rotational power of the outer ring to the inner ring,
And a cage formed with a window for supporting the two balls,
The pair of outer ring tracks are inclined by a skew angle? In opposite directions with respect to the joint axis X, and the outer ring tracks formed on the inner surface of the outer ring are formed as one pair.
The inner ring tracks formed on the outer surface of the inner ring correspond to the outer ring tracks of the outer ring forming one pair of two, and the pair of inner ring tracks are inclined by the skew angle in opposite directions with respect to the joint axis line X Wherein the fixed joint is a ball joint. The method according to claim 1,
Wherein the outer ring track is divided into a tapered track having a curved track and a tapered angle, and the two tracks are in contact with each other. The method according to claim 1,
Wherein the inner ring track is divided into a tapered track having a curved track and a tapered angle, and the two tracks are in contact with each other. The method according to claim 1,
Characterized in that the track radius center of the curved track of the outer ring track is offset vertically f from the joint rotation center O and the center of the bore in the outer ring is in contact with the outer radius of the cage at the joint rotation center O Fixed ball type constant velocity joint. The method according to claim 1,
Characterized in that the track radius center of the curved track of the inner ring track is offset vertically f from the joint rotation center O and the center of the bore in the outer ring is in contact with the outer radius of the cage at the joint rotation center O Fixed ball type constant velocity joint. The method according to claim 1,
Wherein the ratio of the outside cage width to the end window width (the outside crotch width / the end window width is 0.85 to 0.95). The method according to claim 1,
Wherein the joint is applied to a joint having eight or more balls.
KR1020130091258A 2013-07-31 2013-07-31 Fixed type constant velocity joint KR20150015324A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020130091258A KR20150015324A (en) 2013-07-31 2013-07-31 Fixed type constant velocity joint

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020130091258A KR20150015324A (en) 2013-07-31 2013-07-31 Fixed type constant velocity joint

Publications (1)

Publication Number Publication Date
KR20150015324A true KR20150015324A (en) 2015-02-10

Family

ID=52571848

Family Applications (1)

Application Number Title Priority Date Filing Date
KR1020130091258A KR20150015324A (en) 2013-07-31 2013-07-31 Fixed type constant velocity joint

Country Status (1)

Country Link
KR (1) KR20150015324A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114746660A (en) * 2019-12-13 2022-07-12 Gkn 动力传动系统国际有限责任公司 Drive shaft arrangement for a motor vehicle
CN117814963A (en) * 2024-03-04 2024-04-05 北京爱康宜诚医疗器材有限公司 Lumbosacral fusion device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114746660A (en) * 2019-12-13 2022-07-12 Gkn 动力传动系统国际有限责任公司 Drive shaft arrangement for a motor vehicle
CN117814963A (en) * 2024-03-04 2024-04-05 北京爱康宜诚医疗器材有限公司 Lumbosacral fusion device

Similar Documents

Publication Publication Date Title
CN102612609B (en) Stationary constant-velocity universal joint
US8814712B2 (en) Sliding ball type constant velocity joint for vehicle
US9255611B2 (en) Constant velocity universal joint
US20130267332A1 (en) Fixed-type constant-velocity universal joint
WO2016147827A1 (en) Tripod constant velocity universal joint
KR20150015324A (en) Fixed type constant velocity joint
KR101187529B1 (en) angled offset ball type constant velocity joint for vehicle
CN105452694B (en) Sliding Rzeppa constant velocity joint for vehicle
CN104832553B (en) CV joint
EP3279491A1 (en) Ball-type cross groove joint
KR101378669B1 (en) sliding ball type contant velocity joint for vehicle
JP2013108616A (en) Sliding ball type constant velocity joint for vehicle
RU106316U1 (en) SPHERICAL HINGE OF EQUAL ANGULAR SPEEDS
JP6658319B2 (en) Fixed constant velocity joint
KR101640305B1 (en) Fixed ball type joint for vehicle
JP6796931B2 (en) Fixed constant velocity universal joint
KR101473575B1 (en) 8ball-type cross grove joint having self-centering function
JP2006207801A5 (en)
CN109139724A (en) Ball retainer for VL universal joint and CG universal joint
RU2548222C2 (en) Cardan shaft with hinges of equal rotational speeds of rolling friction
US11493092B2 (en) Speed-reducing or -increasing apparatus
KR101314447B1 (en) Sliding ball type contant velocity joint for vehicle
KR101378677B1 (en) sliding ball type contant velocity joint for vehicle
KR101538577B1 (en) Cross groove joint
JP2013100881A (en) Constant velocity joint of angle offset ball type for vehicle

Legal Events

Date Code Title Description
A201 Request for examination
E902 Notification of reason for refusal
E90F Notification of reason for final refusal
E601 Decision to refuse application