JP2003307235A - Constant velocity universal joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To miniaturize and to secure strength, load capacity and durability. <P>SOLUTION: Eight torque transmission balls 3 are situated. A ratio 1 (= PCDBALL/DBALL) between a pitch circle diameter PCDBALL and the diameter DBALL of the torque transmission ball is set to a value in a range of 3.3≤r1≤5.0 and a ratio r2 (=DOUTER/PCDSERR) between the outside diameter DOUTER of an outer ring 1 and the pitch circle diameter PCDSERR of a serration (or a spline) 2c of an inner ring 2 is set to a value in a range of 2.5≤r2≤3.5. <P>COPYRIGHT: (C)2004,JPO

Description

DETAILED DESCRIPTION OF THE INVENTION [0001] TECHNICAL FIELD The present invention relates to eight torque transmissions.
The present invention relates to a constant velocity universal joint having a ball. [0002] FIG. 15 shows an example
This is a typical Zepper type constant velocity universal joint.
You. The constant velocity universal joint has six spherical inner surfaces 11a.
Outer joint portion in which a curved guide groove 11b is formed in the axial direction
The outer ring 11 as a material and the spherical outer diameter surface 12a have six
A curved guide groove 12b is formed in the axial direction, and a shaft portion is formed on the inner diameter surface.
(Or spline) 12 for connecting
c, an inner ring 12 as an inner joint member, and an outer ring 1
1 and the guide groove 12b of the inner ring 12 cooperate with each other.
Arranged on each of the six ball tracks formed
Six torque transmission balls 13 and torque transmission balls 13
And a holder 14 for holding the The center A of the guide groove 11b of the outer race 11 is an inner diameter surface.
11a of the guide groove 12b of the inner ring 12 with respect to the center of the spherical surface
The center B is, with respect to the spherical center of the outer diameter surface 12a, respectively,
On the opposite side by the same distance in the axial direction (center A is the opening side of the joint,
The center B is offset (to the far side of the joint). That
Therefore, the guide groove 11b and the corresponding guide groove 12b
The cooperating ball track is located on the open side of the joint.
It becomes a wedge-shaped open shape. Guide surface of cage 14
Inner surface 11a of the outer ring 11 and outer surface of the inner ring 12
The center of the spherical surface of the torque transmission ball 13
It is in the joint center plane O including the center. The outer race 11 and the inner race 12 change their angle by an angle θ.
The torque transmitting ball 1 guided by the cage 14
3 is always the bisector of angle θ at any operating angle θ
(Θ / 2) is maintained, so the constant velocity of the joint is ensured
Is done. The present invention relates to a constant velocity universal joint as described above.
In order to further reduce the size,
(Equal to or equal to (6 ball constant velocity universal joint as described above))
Aims to ensure high strength, load capacity and durability
And [0006] Means for Solving the Problems To solve the above problems,
Therefore, the present invention provides a plurality of axially extending spherical inner surfaces.
An outer joint member with a guide groove and a shaft on a spherical outer diameter surface
An inner joint member formed with a plurality of guide grooves extending in the direction,
Guide groove of outer joint member and corresponding inner joint member
For multiple ball tracks formed in cooperation with guide grooves
The torque transmission balls and the torque transmission balls
A ball holder for holding the ball,
The constant velocity universal joint opened in a wedge shape in one of the directions
The number of ball tracks and the arrangement of torque transmitting balls.
The number was set to 8. In the above configuration, the torque transmission ball pin
Switch diameter (PCD_BALL) And diameter (D _BALL) And r1
(= PCD_BALL/ D_BALL) Is set to 3.3 ≦ r1 ≦ 5.0.
Can be Here, the pitch circle diameter of the torque transmitting ball
(PCD_BALL) Is in the guide groove of the outer joint member (outer ring)
Center of center or guide groove of inner joint member (inner ring) and torque transmission
Length of the line connecting the center of the ball
Between the center of the guide groove of the ring) and the center of the torque transmission ball
The length of the line segment and the center of the guide groove of the inner joint member (inner ring)
The length of the line connecting the center of the torque transmitting ball is equal to
No. Thereby, the constant velocity of the joint is ensured. Below,
Is referred to as (PCR). ｝ Twice (PCD_BALL= 2
× PCR). The reason for setting 3.3 ≦ r1 ≦ 5.0 is that the outer ring
Comparison of strength, load capacity and durability of joints (Fig. 1
6 ball constant velocity universal joint as shown in 5) or more
This is to ensure. That is, the constant velocity universal joint
Of the torque transmitting ball in a limited space
Pitch circle diameter (PCD_BALLDifficult to change significantly)
It is. Therefore, the value of r1 mainly depends on the torque transmitting ball.
Diameter (D_BALL). r1 <3.3
Is (mainly the diameter D_BALLIs larger), other parts
(Outer ring, inner ring, etc.) is too thin, and in terms of strength
Concerns arise. Conversely, if r1> 5.0 (mainly the diameter
D_BALLIs small), the load capacity is small, and the durability is low.
Concerns arise in terms of: Also, torque transmission balls and guide grooves
Surface pressure at the contact portion with the_BALLBecomes smaller
And the contact ellipse in the contact area is smaller)
There is a concern that it may cause chipping of the groove shoulder edge.
You. By setting 3.3 ≦ r1 ≦ 5.0,
Comparison of strength of outer ring, load capacity and durability of joint
(Six balls) or more. This
This has been supported to some extent by tests. [0011] [Table 1]As shown in Table 1, (Table 1 is based on a comparative test.
It shows the evaluation. ), When r1 = 3.2
The strength of the outer ring, inner ring and cage is not
Unsatisfactory results were obtained. r1 = 3.3, 3.4
Good results are obtained in terms of strength.
Was. In particular, when r1 ≧ 3.5, the outer ring, the inner ring,
The strength of the cage and the durability of the joint are sufficiently ensured,
Good results were obtained. Note that r1> 3.9.
Has not been tested yet, but is as good as above.
It is assumed that good results are obtained. Where r
1> When 5.0, the durability and inner
・ Because the strength of the outer ring is considered to be a problem, r1
It is better to set ≦ 5.0. As described above, r1 is 3.3 ≦ r1 ≦ 5.
0, preferably in the range of 3.5 ≦ r1 ≦ 5.0
Good to set. Further, the pitch circle diameter (P
CD_BALL) And diameter (D_BALL) And r1 (= PCD)_BALL
/ D_BALL) Is set to 3.3 ≦ r1 ≦ 5.0, and
Outer diameter of side joint member (D_OUTER) And the tooth shape of the inner joint member
(Tooth pattern for connecting the shaft. On the inner diameter surface of the inner joint member.
It is formed. ) Pitch circle diameter (PCD_SERR) And r2
(= D_OUTER/ PCD_SERR) With 2.5 ≦ r2 ≦ 3.5
can do. The reason why 3.3 ≦ r1 ≦ 5.0 is as described above.
The same is true. As a preferred range, 3.5 ≦ r1
The same holds true for ≦ 5.0. 2.5 ≦ r2 ≦ 3.
The reason for setting 5 is as follows. That is, the teeth of the inner joint member
Mold pitch diameter (PCD_SERR) Indicates the strength of the mating shaft
It cannot be changed drastically in relations. Therefore, r2
Is mainly determined by the outer diameter of the outer joint member (D_OUTERDepends on)
Will be. If r2 <2.5 (mainly the outer diameter D
_OUTERIs small), the thickness of each part (outer ring, inner ring, etc.)
Becomes too thin, which raises concerns about strength. On the other hand, r
2> 3.5 (mainly the outer diameter D_OUTERIs big
Case), a practical problem arises from the viewpoint of dimensions and the like. 2.
By setting 5 ≦ r2 ≦ 3.5, the strength of the outer ring and the like can be improved.
And the durability of the joint is equal to or better than that of the comparison product (6 balls).
And practical requirements can be satisfied.
In particular, by setting 2.5 ≦ r2 <3.2, the same call
And type of comparison product (6 balls: generally r2 ≥ 3.2
You. ), The outer diameter can be reduced.
There are benefits. As described above, r2 is 2.5 ≦ r2 ≦ 3.
5, preferably in the range of 2.5 ≦ r2 <3.2.
Good to set. [0017] BRIEF DESCRIPTION OF THE DRAWINGS FIG.
Therefore, it will be described. As shown in FIG. 1, the constant-speed
The joint has eight curved guide grooves on the spherical inner surface 1a.
Outer ring 1 as outer joint member formed with 1b in the axial direction
And eight curved guide grooves 2b on the spherical outer diameter surface 2a.
It is formed in the axial direction and is a selector for connecting the shaft portion 5 to the inner diameter surface.
Inner joint part with the formation (or spline) 2c
Inner ring 2 as material and guide groove 1b of outer ring 1 and corresponding
Guide grooves 2b of the inner ring 2 are formed in cooperation with each other.
Eight torque transmission bolts respectively arranged on the ball track
Between the ball 3 and the retainer 4 for holding the torque transmitting ball 3.
Be composed. In this embodiment, the guide groove 1 of the outer race 1
the center O1 of the inner ring 2 with respect to the center of the spherical surface of the inner surface 1a.
Center O2 of the guide groove 2b of
On the opposite side by an equal distance (F) in the axial direction (middle
The center O1 is on the opening side of the joint, and the center O2 is on the back side of the joint.
Has been offset. Therefore, the guide groove 1b and the
A ball track formed in cooperation with a corresponding guide groove 2b.
The wedge shape is open toward the open side of the joint.
You. The center of the spherical surface of the outer diameter surface 4a of the cage 4 and
And the inner diameter of the outer ring 1 serving as a guide surface for the outer diameter surface 4a of the cage 4.
The spherical center of the surface 1a is
It is in the joint center plane O including the center O3. In addition, cage 4
Center of the spherical surface of the inner diameter surface 4b and the inner diameter surface 4 of the cage 4
The center of the spherical surface of the outer diameter surface 2a of the inner ring 2 serving as the guide surface of b
The displacement is also in the joint center plane O. Therefore, the outer ring 1
The offset amount (F) is determined between the center O1 of the guide groove 1b and the inside of the joint.
Axial distance from center plane O, offset amount of inner ring 2
(F) is between the center O2 of the guide groove 2b and the joint center plane O.
And the two are equal. Guide groove 1 of outer ring 1
b and the center O2 of the guide groove 2b of the inner ring 2 are connected to each other.
Opposite side of hand center plane O by equal distance (F) in axial direction
(The center O1 of the guide groove 1b is on the opening side of the joint,
The center O2 is located at a position shifted toward the back of the joint). Outer ring 1
Center O1 of the guide groove 1b and center O of the torque transmitting ball 3
3 and the center O2 of the guide groove 2b of the inner ring 2
The length of the line connecting the center O3 of the torque transmitting ball 3 is
Each is a PCR, and both are equal. The outer race 1 and the inner race 2 are angularly displaced by the angle θ.
Then, the torque transmission ball 3 guided by the retainer 4 is always
For any operating angle θ, bisecting plane of angle θ (θ / 2)
And the constant velocity of the joint is ensured. As described above, the torque transmitting ball 3
Pitch circle diameter PCD_BALL(PCD_BALL= 2 × PC2R) and
Diameter D_BALLRatio r1 (= PCD_BALL/ D_BALL)
3.3 ≦ r1 ≦ 5.0, preferably 3.5 ≦ r
The value within the range of 1 ≦ 5.0 is the strength of the outer ring, etc.
Preferred from the viewpoint of securing, securing load capacity, and securing durability
However, in this embodiment, r1 is set to 3.83.
You. Also, the outer diameter D of the outer ring 1_OUTERAnd serration of inner ring 2
(Or spline) 2c pitch circle diameter PCD_SERRWhen
Ratio r2 (= D _OUTER/ PCD_SERR) Is 2.5 ≦ r2 ≦
3.5, for example, a value within the range of 2.5 ≦ r2 <3.2
It has been set. In addition, the above configuration may be used alone.
No. With respect to the above configuration, the same call format
Comparative product (constant speed universal joint of 6 balls as shown in Fig. 15)
Table 2 shows the comparison with hand). [0024] [Table 2] The constant velocity universal joint of this embodiment has a torque transmission
Comparable product (6 balls) with 8 balls 3
Torque transmission ball 1 in the total load capacity of the joint
Since the load ratio per unit is small, a comparison product of the same nominal type
(6 balls), the diameter D of the torque transmitting ball 3
_BALLAnd reduce the thickness of outer ring 1 and inner ring 2
It is possible to secure as much as a comparison product (6 balls)
You. A comparative product of the same nominal type (6 baud
To the ratio r2 (= D_OUTER/ PCD_SERR) Small
Comb (2.5 ≦ r2 <3.2), comparison product (6 pieces
The strength, load capacity and durability equal to or better than
In addition, the size can be further reduced. FIG. 2 shows the outer race 1. Outer ring 1
In the opening side area of the radial surface 1a, the retainer 4 is assembled on the inner diameter surface 1a.
A cylindrical cut portion 1a1 is provided for insertion. Security
When assembling the holder 4, as shown in FIG.
With the axes perpendicular to each other, the pocket 4
c is put into the cylindrical cut portion 1a1. In this manner, hold
The center of the spherical surface of the outer diameter surface 4a is the inner diameter surface 1 of the outer ring 1.
Insert until it matches the spherical center of a. From this state,
The retainer 4 is rotated by 90 degrees, and the axis of the retainer 4 is
Align with the axis. As a result, the retainer 4
It is completely incorporated into the inner diameter surface 1a. FIGS. 2C and 2D are enlarged views.
As shown in FIG.
1b1 is provided. Guide 1b1
When heat-treating groove 1b {heat is applied to region W in FIG.
Perform processing.役 割 has the role of preventing burn-through (outer ring 1
At the same time to prevent burning in the open end face of the
When assembling the luk transmission ball 3 into the pocket 4c of the retainer 4
Can be used as a guide. FIG. 3 shows the inner race 2. Outside the inner ring 2
The diameter of the radial surface 2a is A, and the two guide grooves 1 opposed by 180 degrees.
outer diameter surface in a vertical section parallel to the plane S including the groove bottom of b
The maximum interval between 2a is C. FIG. 4 shows the retainer 4. Cage 4
Have eight window-like housings for holding and holding the torque transmitting balls 3.
The pockets 4c are provided at equal circumferential intervals. Eight ports
Four of the sockets 4c are long pockets having a large circumferential dimension.
4c1, the remaining four small short pockets 4 in the circumferential direction
c2, long pocket 4c1 and short pocket 4c2 alternate
Are arranged. In addition, of the retainer 4 for incorporating the inner ring 2
The diameter (B) of the inlet 4d is the outer diameter of the inner ring 2 shown in FIG.
(A) and the maximum interval (C), C ≦ B <A
It is set to be. The back side of the entrance 4d (inner diameter
The boundary between the surface 4b and the entrance 4d) is a step 4e.
I have. The diameter (B) of the inlet 4d is determined by the relation of C ≦ B <A.
Is set on the inner diameter surface 4b of the retainer 4.
This is because the incorporation of the wheel 2 has been considered. Inner ring
When assembling the two, the axes of each other are orthogonal
Then, one guide groove 2b of the inner ring 2 is connected to the entrance 4d of the retainer 4.
And insert the inner ring 2 into the inner diameter surface 4b of the retainer 4.
Enter. In this manner, when the inner ring 2 is inserted to some extent,
The maximum distance (C) between the outer diameter surfaces 2a of the wheel 2 is caught on the step 4e.
The inner ring 2 can no longer be inserted
(State shown in FIG. 5). From this state, rotate inner ring 2 90 degrees
To make the axis of the inner ring 2 coincide with the axis of the cage 4.
You. As a result, the inner ring 2 is completely on the inner diameter surface 4b of the retainer 4.
Incorporated in. Four long pockets 4c1 and four short pockets
4c2 and the torque transmitting balls 3
Consideration of the incorporation when assembling into the pocket 4c of the retainer 4.
Because he did. As shown in FIG.
The ball 3 is assembled by assembling the inner ring 2 and the cage 4.
After assembling the yellowtail into the inner surface 1a of the outer ring 1, the inner ring 2 and
The cage 4 is angularly displaced with respect to the outer race 1 (the ball assembling angle).
α). In each phase of FIG.
The torque transmitting balls 3 are indicated by 31, 32,.
You. The torque transmission balls 31, 33, 35, 37 are cages
4 is stored in the short pocket 4c2,
2, 34, 36 and 38 are accommodated in the long pocket 4c1
I have. In the pocket 4c when the joint has the operating angle α
The moving position of the torque transmitting ball 3 is as shown in FIG.
become. FIG. 7A shows the setting of the cage offset (f).
FIG. 7 (b) shows the cage offset,
11 and 12 provided with (f).
I am responding. First, the torque transmitting ball 3 has four long pockets.
4c1 each, then 4 short pockets
4c2. For example, torque transmitting ball 3
1 is incorporated, the phases 33, 35, 37
The amount of movement of the reaching ball 3 in the circumferential direction is small. Therefore, Tor
The transmission ball 31 can be incorporated into the short pocket 4c2.
Wear. Similarly, for example, incorporating the torque transmission ball 33
At this time, in the phases of 31, 35 and 37, the torque transmitting ball 3
Has a small amount of movement in the circumferential direction. Therefore, the torque transmission
Can be assembled in the short pocket 4c2. this
In this way, all short pockets 4c2 are
3 can be incorporated. In addition, the torque transmitting ball 3
When assembled in the pocket 4c, the chamfer 1b1 of the outer ring 1
It plays the role of guiding the torque transmitting ball 3 (FIG. 6A)
reference}. In the manner described above, the outer ring 1, the inner ring 2, and the cage
4. When the torque transmitting ball 3 is assembled, the actual ball shown in FIG.
The constant velocity universal joint of the embodiment is completed. Serration of inner ring 2
The shaft portion 5 is connected to the shaft (may be a spline) 2c.
It is. In this embodiment, the shaft 5 is formed of boron steel.
The diameter of the shaft 5 is reduced (when the maximum operating angle is given,
The diameter of the portion that interferes with the open end of the outer ring 1 is reduced.
The serration diameter is the same as the comparative product. ). Shaft
The reason for reducing the diameter of 5 was to consider the increase in operating angle.
is there. For prototypes, for example, for drive shafts of automobiles
Fully achieves the maximum operating angle of 45 ° required for joints
did it. FIG. 8 shows an embodiment product and a comparative product (six balls).
Constant velocity universal joints) (all have the same nominal type)
Compare the relationship between rotation speed (rpm) and temperature rise (° C)
The test results are shown. In the figure, X (dotted white circle) is an actual
The embodiment product, Y (solid black circle) is a comparative product, and the amount of temperature rise
(° C) is the data measured 30 minutes after the start of operation.
It is. Θ is the joint operating angle, and T is the input rotational torque.
It is. As is clear from the test results shown in FIG.
The temperature rise of the embodiment product (X) is smaller than that of the comparison product (Y).
Well, the difference increases as the number of rotations increases
I have. Reducing the temperature rise leads to improved durability. Ma
Also, such a reduction in temperature rise is due to the operating angle (θ) and
Considered that it can be obtained regardless of the input rotation torque (T)
available. FIG. 9 shows an embodiment product and a comparative product (6 boads).
) (Both have the same nominal type)
It shows the results of a comparative test of changes over time in (° C).
In the figure, X (dotted white circles) is the embodiment product, and Y (solid line black circles) is
Is a comparison product, θ is the joint operating angle, and T is the input rotational torque.
is there. As is clear from the test results shown in FIG.
The temperature rise of the embodiment product (X) is smaller than that of the comparison product (Y).
Well, the difference changes very much even if the driving time is long
Not in. FIG. 10 shows an embodiment product and a comparison product (6 bauds).
Operating angle θ (d
eg) and the torque loss rate (%)
The result is shown. In the figure, X (dotted white circle) indicates the product of the embodiment,
Y (solid black circle) is a comparative product, and is input at θ = 10 deg.
Force rotation torque T = 196 N · m, θ = 30 deg.
= 98 N · m, and the torque loss rate is measured. As is apparent from FIG.
The torque loss rate of (X) is smaller than that of comparative product (Y).
The difference increases as the moving angle θ increases.
You. Reduction of torque loss contributes to fuel saving and energy saving
In addition to reducing the temperature rise and improving the durability.
To Table 3 shows the embodiment product and the comparison product (6 pieces
) (For the same call format) for 300 hours
Observe the damage of outer ring, inner ring, cage and ball after rolling
The results are shown. As for the retainer,
The wear depth was measured and the result is shown in FIG. Trial
The test conditions were as follows: θ = 6 deg, T = 1078 Nm, rotation speed
= 200 rpm, total rotation speed = 3.60 × 10 6 (re
v). Note that the test was performed as the embodiment product and the comparative product.
The test was performed using two test pieces (the product in the embodiment is NO
1, 2, comparative products are NO3, 4), wear depth shown in Fig. 11
Is the average of two test articles. [0041] [Table 3] As is evident from the results shown in Table 3,
No damage to each part, both in the form and in the comparison
Was. Also, as is clear from the results shown in FIG.
Wear depth of the cage pocket in the form (X)
Was smaller than the comparative product (Y). As described above, the constant velocity universal joint of this embodiment
According to the hand, it is a comparative product despite its compact shape
(6 balls) or more load capacity and
It can have durability. FIG. 12 relates to another embodiment of the present invention.
3 shows a constant velocity universal joint. Center of guide groove 1b of outer ring 1
O1 is a plan of the inner ring 2 with respect to the spherical center O4 of the inner diameter surface 1a.
The center O2 of the inner groove 2b is in relation to the center O5 of the spherical surface of the outer diameter surface 2a.
And off to the opposite side by an equal distance (F) in the axial direction, respectively.
Is set. Further, in this embodiment, the cage
4 center of the spherical surface of the outer diameter surface 4a (the spherical surface of the inner diameter surface 1a of the outer ring 1).
Center O4) and the spherical center of the inner diameter surface 4b of the retainer 4.
(Same as the spherical center O5 of the outer diameter surface 2a of the inner ring 2).
Opposite side of hand center plane O by equal distance (f) in axial direction
Offset. Offset amount of outer ring 1
(F) shows the center O1 of the guide groove 1b and the center O4 of the inner diameter surface.
, The offset amount of the inner ring 2 (F)
Is the center O2 of the guide groove 2b and the spherical center O5 of the outer diameter surface 2a.
And the two are equal. Outer ring 1 plan
The center O1 of the inner groove 1b and the center O2 of the guide groove 2b of the inner ring 2
Is on the opposite side of the joint center plane O by the same distance in the axial direction.
(The center O1 of the guide groove 1b is on the opening side of the joint,
The center O2 is located at a position shifted toward the back of the joint). Outer ring 1
Center O1 of the guide groove 1b and center O of the torque transmitting ball 3
3 and the center O2 of the guide groove 2b of the inner ring 2
The length of the line connecting the center O3 of the torque transmitting ball 3 is
Each is a PCR, and both are equal. In the above embodiment,
Configuration is the same, so the description is omitted.
I do. The embodiment shown in FIG.
1b, a predetermined region U1 of the guide groove 2b of the inner ring 2
2 is a straight shape. Guide groove 1
The area other than U1 in b is a curve centered on the point O1,
The area other than U2 of the groove 2b has a curved shape centered on the point O2.
is there. Other configurations are the same as those of the above-described embodiment.
Therefore, the description is omitted. In this type of constant velocity universal joint, the outer ring
Center of guide groove, center of inner ring guide groove, inside spherical surface of outer ring inner diameter surface
FIG. 14 shows the positional relationship between the center of the spherical surface of the inner and outer diameter surfaces of the inner ring.
Eight variations as shown in FIGS. 14 (a) to 14
(H) Although there is｝, the present invention is applicable to any of the configurations.
can do. By the way, the configuration of FIG.
14 (b) and the configurations of FIGS. 12 and 13 are shown in FIG. 14 (a).
Each is supported. Further, according to the present invention, the inner ring and the shaft portion are formed with
Configuration or spline)
Not only for joints, but also for
It is also applicable to existing joints. For example, inner rings, cages,
After incorporating the ball and ball into the outer ring, align the shaft with the end
Joined to the body (welding, eg laser beam welding, pressure welding, etc.)
It is also possible to adopt a configuration in which Further, the constant velocity universal joint of the present invention
Widely used as power transmission element in various industrial machines
be able to. [0049] As described above, according to the present invention,
Further downsizing of constant velocity universal joints
At the same time as the comparable product (6 balls)
On top strength, load capacity and durability can be ensured
You.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view (FIG. A: FIG. B) showing an embodiment of the present invention.
2 is a sectional view taken along a line a-a in FIG. 2, and a cross-sectional view is shown in FIG. FIG. 2 is a front view of the outer race (FIG. A), a vertical partial cross-sectional view (FIG. B), an enlarged front view of a guide groove portion in FIG.
It is an expanded longitudinal cross-sectional view (FIG. D) of the end part in FIG. B. FIG. 3 is a front view (FIG. A) and a longitudinal sectional view (FIG. B) of the inner race. FIG. 4 is a cross-sectional view (FIG. A) and a vertical cross-sectional view (FIG. B) of the cage.
It is. FIG. 5 is a front view showing an embodiment when the inner ring is assembled into the retainer. FIG. 6 is a longitudinal sectional view (FIG. A) and a transverse sectional view (FIG. B) showing an aspect when a torque transmitting ball is incorporated. FIG. 7 is a diagram showing a moving position of a torque transmitting ball in a pocket at an operating angle α. FIG. 7A corresponds to a configuration without a cage offset, and FIG. 7B corresponds to a configuration with a cage offset. FIG. 8 is a diagram showing the relationship between the number of rotations and the amount of temperature rise (FIGS. A, b, and c). FIG. 9 is a diagram showing a change over time in the amount of temperature rise. FIG. 10 is a diagram showing a relationship between an operating angle and a torque loss rate. FIG. 11 is a view showing a result of measuring a wear depth of a pocket portion of the cage. FIG. 12 is a longitudinal sectional view (FIG. A: a-a section in FIG. B) and a transverse sectional view (FIG. B: FIG. A) showing another embodiment of the present invention.
Bb section). FIG. 13 is a vertical sectional view (FIG. A: a-a section in FIG. B) and a transverse sectional view (FIG. B: FIG. A) showing another embodiment of the present invention.
Bb section). FIG. 14 shows the center of the outer ring guide groove in the constant velocity universal joint,
It is a figure which shows the variation of the positional relationship of the center of an inner ring guide groove, the center of an outer ring inner diameter surface (retainer outer diameter surface), and the center of an inner ring outer diameter surface (retainer inner diameter surface). FIG. 15 is a cross-sectional view (FIG. A) and a vertical cross-sectional view (FIG. B: b- in FIG. A) showing a comparative product (constant velocity universal joint of six balls).
(b sectional view). [Description of Signs] 1 Outer ring 1a Inner diameter surface 1b Guide groove 2 Inner ring 2a Outer diameter surface 2b Guide groove 3 Torque transmitting ball 4 Cage

Continuation of front page    (72) Inventor Tatsuro Sugiyama             3070-1 found in Iwata City, Shizuoka Prefecture

Claims (1)

Claims: 1. An outer joint member having a plurality of axially extending guide grooves formed on a spherical inner diameter surface, and a plurality of axially extending guide grooves formed on a spherical outer diameter surface. Inner joint member,
A torque transmission ball disposed on each of a plurality of ball tracks formed by a guide groove of the outer joint member and a corresponding guide groove of the inner joint member, and a retainer holding the torque transmission ball. A constant velocity universal joint, wherein the ball tracks are opened in a wedge shape toward one of the axial directions, wherein the number of the ball tracks and the number of the torque transmitting balls are eight.