US20030017877A1

US20030017877A1 - Constant velocity universal joint

Info

Publication number: US20030017877A1
Application number: US10/124,732
Authority: US
Inventors: Masazumi Kobayashi; Kazuhiro Azuma; Tohru Nakagawa; Isamu Tanimoto; Katsuyuki Ikei; Hisaaki Kura
Original assignee: NTN Corp
Current assignee: NTN Corp
Priority date: 2001-04-24
Filing date: 2002-04-18
Publication date: 2003-01-23
Also published as: US20050261067A1; FR2823815A1; US7097567B2; FR2823815B1

Abstract

A novel constant velocity universal joint with eight ball is provided for realizing the improved durability of the joint under high-loaded conditions and the suppressed variations of lifetimes of the joints. The universal joint has an outer joint member having eight curved track grooves axially extending along an inner circumferential surface with a spherical shape, an inner joint member having eight curved track grooves axially extending along an outer circumferential surface with a spherical shape, eight balls respectively arranged in eight ball tracks provided as pairs of the track grooves of the outer joint member and the track grooves of the inner joint member, and a cage having pockets for respectively holding the balls. The center of each track groove of the outer joint member is axially displaced a predetermined distance from the spherical center of the inner circumferential surface. The center of each track groove of the inner joint member is axially displaced the same distance from the spherical center of the outer circumferential surface in the direction opposite to that of the outer joint member. A PCD gap in the ball track is in the range of 5 μm to 50 μm.

Description

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to fixed-type constant velocity universal joints to be used in power transmission systems of automobiles and various kinds of industrial machines, each of which only allows an operational angle displacement between a shaft on the power-transmitting side and a shaft on the driven side.

2. Description of the Related Art

Fixed-type constant velocity universal joints (e.g., Rzeppa constant velocity universal joints well known as Birfield universal joints: BJs) have been used for the connection between drive shafts or the like in automobiles. Typically, the conventional fixed-type constant velocity universal joint (hereinafter, simply referred to as the conventional universal joint) comprises: an outer joint member in which curved track grooves are axially formed on its inner circumferential surface with a spherical shape; an inner joint member in which curved track grooves are axially formed on its outer circumferential surface with a spherical shape; a plurality of balls respectively arranged in ball tracks provided as pairs of track grooves of the inner and outer joint members; and a cage having pockets for respectively holding these balls. More specifically, the plurality of balls are arranged in their respective pockets of the cage at regular intervals in a circumferential direction of the joint.

The center of the track groove of the outer joint member is displaced a predetermined distance from the spherical center of the inner circumferential surface. On the other hand, the center of the track groove of the inner joint member is displaced the same distance from the spherical center of the outer circumferential surface in the direction opposite to that of the outer joint member. Here, such a displacement is referred to as a track offset. Therefore, the ball track formed between the outer joint member and the inner joint member is shaped like a wedge opened toward one end of the joint in the axial direction. In addition, the spherical center of the inner circumferential surface of the outer joint member and the spherical center of the outer circumferential surface of the inner joint member are located within a common plane, i.e., the central plane of the joint that includes the center of each ball.

In the conventional universal joint, the constant velocity of the joint can be ensured because each of the ball held in the pocket of the cage can be always located in a plane that bisects any operational angle when there is an angular displacement between the outer joint member and the inner joint member. Here, the operational angle refers to an angle formed by a rotational axis of the outer joint member and a rotational axis of the inner joint member.

In recent years, there may be cases where a wheel base is lengthened from the viewpoint of improving the safety of automobile in the event of a crash. In this case, however, there is a need to increase a steering angle for front wheels by providing the universal joint with a higher operation angle. For filling the need for such a higher-angle, there is provided another conventional universal joint, i.e., an undercut-free type universal joint (UJ) in which the track grooves on the opening side of the outer joint member are shaped so as to be in parallel with the axial direction of the joint. In this kind of the universal joint, there is no under cut formed on either of the outer joint member or the inner joint member so that a higher operation angle can be attained.

In each kind of the conventional universal joints (BJ, UJ), it is very important to define how to fill a gap between a pitch circle diameter of the track groove of the outer joint member and a pitch circle diameter of the track groove of the inner joint member (hereinafter, such a gap is referred to as a PCD gap). If the PCD gap is too small, it becomes difficult to insert balls into the respective ball tracks and each of the balls is then difficult to roll smoothly as the binding force upon the ball increases. During the rotation of the universal joint, the rolling movement of the ball is caused with sliding contact between the ball and the ball track. As a result of frictional heating, the temperature in the joint increases and hence the lifetime of the joint decreases. If such a gap is too large, on the other hand, the characteristic features of the joint (such as NVH, durability) can be affected by the generation of slapping sounds between the pocket and the ball, or more the increase in vibrations of the joint.

Especially, under high-load conditions, the contact ellipse between the ball and the track groove runs off the track groove. Under such circumstances, it could be chipped from such a portion, resulting in flaking. If the PCD gap is small, it is effective to prevent the contact ellipse from running off the track groove. On the other hand, if such a gap is substantially larger than usual, the ball contact point approaches the PCD gap and hence the contact ellipse becomes easy to run off the track groove.

In each of the conventional universal joints (BJ, UJ), furthermore, it is very important to determine the ratio (F/PCR) between the amount of track offset (F) and the length (PCR) of a straight line segment between the center of the track groove in the outer or inner joint member and the center of the ball. In Japanese Patent Laid-Open Publication No. Hei. 9-317784 (1997), for example, there is disclosed an appropriate range of F/PCR (i.e., 0.069≦F/PCR≦0.121). In this case, the depth of the track groove becomes shallow if the amount of track offset (F) is too large. Thus, the contact ellipse between the ball and the track groove tends to run off the track groove, causing the decrease in allowable load torque at a higher operational angle region. In addition, columns of the cage become narrow, so that the strength of the cage can be also decreased. On the contrary, if the amount of track offset (F) is too small, the track load increases. It causes the decrease in the durability of the joint in addition to lowering of the maximum operational angle.

Typically, the conventional universal joint has six balls (hereinafter, such a joint will be also referred to as a six-ball joint). However, there is an alternative universal joint having eight balls for the purpose of realizing a smaller and lighter version of the joint while retaining at least the same properties (e.g., strength, load capacity, and durability) as those of the joint using six balls. Here, the universal joint having eight balls will be also referred to as an eight-ball joint. The eight-ball joint has its own basic configuration different from that of the six-ball joint. In this case, the set value of the PCD gap may be peculiar to such a configuration. The amount of track offset (F) and the length (PCD) of a straight line segment between the center of the track groove of the outer or inner joint member and the center of the ball are also adjusted such that the ratio F/PCR can be defined within the above appropriate range. It is noted that the depth of the track groove of the eight-ball joint is smaller than that of the six-ball joint as the diameter of each of the eight balls is smaller than that of the six balls. In the eight-ball joint, the PCD gap exerts a very large influence on the durability of the joint. Consequently, there is a limit to improve the durability of the eight-ball joint by means of adjusting the above F/PCR in the appropriate range.

SUMMARY OF THE INVENTION

It is an object of the present invention is to provide an eight-ball joint with the improved durability under high-loaded conditions, which minimize the variations in lifetimes of the joints.

According to a fist aspect of the present invention, there is provided a constant velocity universal joint comprising: an outer joint member having eight curved track grooves axially extending along an inner circumferential surface with a spherical shape; an inner joint member having eight curved track grooves axially extending along an outer circumferential surface with a spherical shape; eight balls respectively arranged in eight ball tracks provided as pairs of the track grooves of the outer joint member and the track grooves of the inner joint member; and a cage having pockets for respectively holding the balls, where a center of each track groove of the outer joint member is axially displaced a predetermined distance from a spherical center of the inner circumferential surface, while a center of each track groove of the inner joint member is axially displaced the same distance from a spherical center of the outer circumferential surface in a direction opposite to that of the outer joint member, wherein a PCD gap in the ball track is in a range of 5 μm to 50 μm. Here, the “PCD gap” refers to the difference between a pitch circle diameter of the track groove of the outer joint member and a pitch circle diameter of the track groove of the inner joint member. The present invention can be applied to a constant velocity universal joint with each of track grooves of the outer and inner joint members having a linear bottom as a straight portion.

According to the first aspect of the present invention, the PCD gap in the ball track is set in the range 5 μm to 50 μm, so that under high-load conditions the contact ellipse between the ball and the track groove is difficult to run off the track groove. Therefore, it becomes possible to easily prevent the generation of chipping or flaking, allowing the increase in the durability and also stabilizing the variations in life of the universal joints. Especially, in the case of the eight-ball joint, the durability can be significantly improved by the PCD gap because of a smaller diameter of the ball that allows a relatively shallow depth of the track groove.

In the first aspect of the present invention, it is preferable to make a gap between the pocket of the cage and the ball in an axial direction so as to be in a range of −30 μm to +10 μm. There is a wearing down of the wall of the pocket of the cage in the axial direction because of the contact between the ball and the wall, so that the gap in the axial direction may excessively increase as long as it is continuously used, except at the early stages. Furthermore, the dimensions of each structural components of the universal joint have unavoidable dimensional variations within manufacturing tolerance.

In the eight-ball joint in accordance with the first aspect of the present invention, the abrasion loss of the pocket is comparably small as the load to be applied on the pocket with respect to one ball is smaller than that of the six-ball joint. Therefore, the smooth rolling of the ball can be ensured with reducing the binding force of the ball in the pocket. That is, the gap in the axial direction is positively shifted with respect to that of the six-ball joint (a gap in the axial direction of −50 μm to −10 μm). Thus, the gap in the axial direction in accordance with the present invention may be in the range of −30 μm to +10 μm, preferably in the range of −10 μm to +10 μm, for preventing the increase in temperature of the inside of the joint by lowering the amount of heat liberated from the contact between the ball and the pocket. As a result, the durability of the joint can be increased.

In the above configuration of the universal joint, the gap between the cage and the outer joint member or between the cage and the inner joint member in a radial direction of the joint may be in a range of 20 μm to 100 μm. Therefore, the operating characteristics between the cage and the outer joint member or between the cage and the inner joint member can be improved. In addition, the generation of slapping sounds between the cage and the outer joint member or between the cage and the inner joint member can be prevented. Furthermore, the increase in vibrations of the joint can be also prevented.

In a second aspect of the present invention, there is provided a constant velocity universal joint; comprising: an outer joint member having eight curved track grooves axially extending along an inner circumferential surface with a spherical shape; an inner joint member having eight curved track grooves axially extending along an outer circumferential surface with a spherical shape; eight balls respectively arranged in eight ball tracks provided as pairs of the track grooves of the outer joint member and the track grooves of the inner joint member; and a cage having pockets for respectively holding the balls, where a center of each track groove of the outer joint member is axially displaced a predetermined distance from a spherical center of the inner circumferential surface, while a center of each track groove of the inner joint member is axially displaced the same distance from a spherical center of the outer circumferential surface in a direction opposite to that of the outer joint member, wherein a ratio (F/PCR) of an amount (F) of displacement (i.e., the amount of track offset) and a length (PCR) of a line segment between the center of the track groove of the outer joint member or the center of the track groove of the inner joint member and a center of the ball is in a range of 0.069≦F/PCR≦0.121, and a contact angle of each of the track grooves of the outer joint member and the inner joint member and the corresponding ball is 37° or less. Also, the present invention is applicable to a constant velocity universal joint where each of the track grooves of the outer joint member and the inner joint member has a bottom with a linear shape provided as a straight portion.

The second aspect of the present invention is predicted on the universal joint being designed to have an appropriate ratio (F/PCR) of the amount (F) of the displacement (i.e., the amount of track offset) and the length (PCR) of a line segment between the center of the track groove of the outer joint member or the center of the track groove of the inner joint member and the center of the ball in the range of 0.069≦F/PCR≦0.121, as disclosed in Japanese Patent Laid-Open Publication No. Hei. 9-317784 (1997). Thus, the present invention is constructed such that a contact angle of each of the track grooves of the outer joint member and the inner joint member and the corresponding ball is 37° or less and the ratio F/PCR is appropriately defined in the above range. Therefore, the contact ellipse between the ball and the track groove becomes difficult to run off the track groove. In addition, there is no clearance of the ball in the ball track at an operational angle less than a normal angle to be applied in the automobile or the like, avoiding the generation of slapping sounds.

By narrowing the contact angle between the track groove and the ball, therefore, the pressure on the contact surface between the track groove and the ball can be increased. However, if the contact angle becomes too small, the durability of the joint may be decreased. For that reason, the lower limit of the contact angle between the track groove and the ball may be defined such that the pressure on the contact surface at the time of loading the basic torque becomes 2.7 GPa or less. Consequently, the durability of the universal joint of the present invention is equal to or more excellent than that of the conventional universal joint. Here, the term “basic torque” means torque that allows a lifetime of 1,500 hours at 100 rpm with a torque value defined from the contact stress (Herz's stress) between the track groove and the ball (basic torque used for the calculation of lifetime of the universal joint).

Here, it is preferable to define the contact angle between the track groove and the ball in a range of 29° to 37°. Therefore, when the contact angle between the track groove and the ball is 29° or more, the pressure on the contact surface between the track groove and the ball can be held under control. Consequently, the durability of the universal joint of the present invention is equal to or more excellent than that of the conventional universal joint.

The nature, principle, and utility of the invention will become more apparent from the following detailed description when read in conjunction with the accompanying drawings in which like parts are designated by like reference numerals or characters.

BRIEF DESCRIPTION OF THE DRAWINGS

In the accompanying drawings: [0023]
FIG. 1 is a cross sectional view taken along the line A-A in FIG. 2 or the line B-B in FIG. 3 for illustrating a constant velocity universal joint as one preferred embodiment of the present invention; [0024]
FIG. 2 is a cross sectional view of the Rzeppa constant velocity universal joint (BJ) as one embodiment of the present invention; [0025]
FIG. 3 is a cross sectional view of the undercut-free constant velocity universal joint (UJ) as another preferred embodiment of the present invention; [0026]
FIG. 4 is a graph that illustrates the results of the endurance test under high-loaded conditions with respect to the PCD gap; [0027]
FIG. 5 is a graph that illustrates the results of the endurance test with respect to the gap in the pocket of the cage in the axial direction; [0028]
FIG. 6 is an enlarged cross sectional view of the main part of the constant velocity universal joint shown in FIG. 3 for explaining the track offset angle; [0029]
FIG. 7 is an enlarged cross sectional view of the main part of the constant velocity universal joint shown in FIG. 3 for explaining the contact angle between the track groove and the ball; and [0030]
FIG. 8 is an enlarged cross sectional view of the main part of the constant velocity universal joint shown in FIG. 3 for explaining the wedge angle.[0031]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

FIG. 2 illustrates a Rzeppa fixed-type constant velocity universal joint (BJ) and FIG. 3 illustrates an undercut-free fixed-type constant velocity universal joint (UJ), respectively. The cross sectional view taken along the line A-A in FIG. 2 and the cross sectional view taken along the line B-B in FIG. 3 are identical to each other, so that FIG. 1 is provided as their common cross sectional view. [0032]
The universal joint (BJ) shown in FIG. 2 as a first embodiment of the present invention comprises an outer [0033] joint member 1 having eight curved track grooves 1 b axially extending along an inner circumferential surface 1 a with a spherical shape; an inner joint member 2 having eight curved track grooves 2 b axially extending along an outer circumferential surface 2 a with a spherical shape and also having a serrated fitting portion 2 c between the end of a middle shaft part 5 of a drive shaft and the inner circumferential surface 1 a, eight balls 3 arranged in respective eight ball tracks formed as pairs of the track grooves 1 b of the outer joint member 1 and the track grooves 2 b of the inner joint member 2, and a cage 4 having pockets 4 c for respectively holding the balls 3 at regular intervals in a circumferential direction.
The center O[0034] ₁of the track groove 1 b of the outer joint member 1 is axially displaced a predetermined distance F from the spherical center of the inner circumferential surface 1 a, while the center O₂of the track groove 2 b of the inner joint member 2 is axially and oppositely (i.e., in the figure, the center O₁is the opening side f the joint, and the center O₂is the recess side of the joint) displaced the same distance F from the spherical center of the outer circumferential surface 2 a (i.e., track offset). Therefore, the ball track formed between the outer joint member 1 and the inner joint member 2 is shaped like a wedge opened to one side in the axial direction (i.e., in the figure, the opening side of the joint).
Both the spherical center of an outer [0035] circumferential surface 4 a of the cage 4 and the spherical center of the inner circumferential surface 1 a of the outer joint member 1 to be provided as a guide surface of the outer circumferential surface 4 a of the cage 4 are located within a central plane O of the joint including the center O₃of the ball 3. In addition, both the spherical center of an inner circumferential surface 4 b of the cage 4 and the spherical center of the outer circumferential surface 2 a of the inner joint member 2 to be provided as a guide surface of the inner circumferential surface 4 b of the cage 4 are located within the central plane O. Therefore, the amount of track offset F in the center O₁of the track groove 1 b in the outer joint member 1 corresponds to the distance from the center O₁to the central plane O of the joint in the axial direction. On the other hand, the amount of track offset F of the center O₂of the track groove 2 b in the inner joint member 2 corresponds to the distance from the center O₂to the central plane O of the joint and is equal to the amount of track offset F in the center O₁of the track groove 1 b.
In this embodiment, furthermore, the spherical centers of the outer [0036] circumferential surface 4 a and the inner circumferential surface 4 b of the cage 4 and the center O₃of the ball 3 are arranged in a line on a common plane perpendicular to the axial direction. Alternatively, these centers may be oppositely displaced the same distance in the axial direction with respect to the center O₃of the ball 3.
The universal joint (UJ) shown in FIG. 3 is another embodiment of the present invention and includes the same structural components except of straight portions U[0037] 1, U2. That is, the straight portion U1 is formed as a liner bottom portion in cross section of the track groove 1 b of the outer joint member 1, while the straight portion U2 is formed as a linear bottom portion in cross section of the track groove 2 b of the inner joint member 2. Therefore, the explanations of the same structural components as those in FIG. 2 will be omitted in the following description. The straight portions U1, U2 formed on the track grooves 1 b, 2 b of the outer joint member 1 and the inner joint member 2 in the universal joint (UJ) of the present embodiment allow the maximum operational angle larger than that of the universal joint (BJ) shown in FIG. 2. In each of the universal joints (BJ, UJ) shown in FIGS. 2 and 3, when the outer joint member 1 and the inner joint member 2 undergo angular displacements with respect to each other, the constant velocity of the joint can be ensured as each of the ball held in the pocket 4 c of the cage 4 can be always located in a plane that bisects any operational angle.
In each of the universal joints (BJ, UJ) shown in FIGS. 2 and 3, furthermore, a PCD gap with respect to the ball track shown in FIG. 1, i.e., the difference between a pitch circle diameter PCD[0038] _OUTof the track groove 1 b of the outer joint member 1 and a pitch circle diameter PCD_INof the track groove 2 b of the inner joint member 2, is defined within the range of 5 μm to 50 μm. If the PCD gap becomes smaller than 5 μm, it becomes difficult to place the balls 3 into the pairs of track grooves 1 b, 2 b and to maintain the stable operation of the joint. If the PCD gap becomes larger than 50 μm, then the improvement in the durability of the joint becomes difficult as the contact ellipse between the ball 3 and the track grooves 1 b, 2 b tends to run off the track grooves 1 b, 2 b.
As shown in FIGS. 2 and 3, furthermore, the gap between the [0039] pocket 4 c of the cage 4 and the ball 3 in the axial direction, i.e., the difference between the axial dimension (D_P) of the pocket 3 and the diameter (D_B) of the ball 3, is defined within the range of −30 μm to +10 μm, preferably of −10 μm to +10 μm. If the interference (negative gap) between the pocket 4 c of the cage 4 and the ball 3 is smaller than −30 μm, the binding force of the ball 3 increases to prevent a smooth rolling movement of the ball 3. During the rotation of the universal joint, therefore, the rolling movement of the ball 3 is caused with sliding contact between the ball 3 and the track grooves 1 b, 2 b. As a result of frictional heating, the temperature in the joint increases and hence the lifetime of the joint decreases. On the other hand, if the clearance (positive gap) between the pocket 4 c of the cage 4 and the ball 3 is larger than +10 μm, undesired effects for the joint performance can be generated. For example, slapping sounds can be generated between the pocket 4 c and the ball 3, or more vibrations can be generated by the joint.
Furthermore, as shown in FIG. 1, the gap between the [0040] cage 4 and the outer joint member 1 in the radial direction (i.e., the difference between the inner diameter (D_O) of the outer joint member 1 and the external diameter (D_K1) of the cage 4) is defined within the range of 20 μm to 100 μm. On the other hand, the gap between the cage 4 and the inner joint member 2 in the radial direction (i.e., the difference between the inner diameter (D_K2) of the cage 4 and the outer diameter (D_I) of the inner joint member 2) is defined within the range of 20 to 100 μm. If each of the gaps in the radial direction is smaller than 20 μm, the operating characteristics between the cage 4 and the outer joint member 1 or between the cage 4 and the inner joint member 2 becomes worse. On the other hand, if each of the gaps in the radial direction is larger than 100 μm, undesired effects for the joint performance can be generated. For example, slapping sounds can be generated between the cage 4 and the outer joint member 1 or between the cage 4 and the inner joint member 2, or more vibrations can be generated by the joint.
For evaluating the above PCD gap, an endurance test under high-loaded conditions was performed on the Rzeppa constant velocity universal joint (BJ) having eight balls as shown in FIG. 2. The results obtained from such a test are listed in FIG. 4. The test was performed using two universal joints A, B as test articles for evaluating each of the different PCD gaps. That is, each of the test joints A, B was driven under the conditions in which load torque T=726 N·m, the number of revolutions N=230 rpm, and operational angle θ=6 deg. Subsequently, the time that elapsed before generating any problem in the test article was measured. [0041]
As is evident from the results shown in FIG. 4, each of the universal joints with PCD gaps of 30 μm and 50 μm ensured the stable durability. On the other hand, each of those with the PCD gaps of 70 μm and 100 μm met the desired spec but expressed variations in lifetimes. In addition, the universal joint with the PCD gap of 120 μm was the limit to meet the desired spec. Furthermore, it was difficult to meet the desired spec when the universal joint with the [0042] PCD gap 130 μm was tested.
For evaluating the gap between the [0043] pocket 4 c of the cage 4 and the ball 3 in the axial direction, an endurance test was performed on the Rzeppa universal joint (BJ) shown in FIG. 2. The results obtained from such a test are listed in FIG. 5. The test was performed using two universal joints A, B as test articles for evaluating each of the joints having different gaps in the axial direction. That is, each of the test joints A, B was driven under the conditions in which load torque T=186 N·m, the number of revolutions N=1700 rpm, and operational angle θ=6 deg. Subsequently, the time that elapsed before generating any problem in the test article was measured.
As is evident from the results shown in FIG. 5, each of the universal joints having the gaps of −20 μm and −30μm in the radial direction ensured the stable durability. On the other hand, the universal joint having the gap of −45 μm in the radial direction showed poor durability and variations in lifetimes. [0044]
In each of the universal joints shown in FIGS. 2 and 3, the length (PCR) of a line segment between the center O[0045] ₁of the track groove 1 b of the outer joint member 1 and the center O₃of the ball 3 is equal to the length (PCR) of a line segment between the center O₂of the track groove 2 b of the inner joint member 2 and the center O₃of the ball 3. In the universal joint shown in FIG. 3, an offset angle which the line segment between the center O₁of the track groove 1 b of the outer joint member 1 and the center O₃of the ball 3 forms with a line segment between the center O of the joint and the center O₃of the ball 3 is defined as β. Similarly, an offset angle which the line segment between the center O₂of the track groove 2 b of the inner joint member 2 and the center O₃of the ball 3 forms with the line segment between the center O of the joint and the center O₃of the ball 3 is also defined as β. Thus, both offset angles are equal to each other.
The amount of track offset (F) of each of the [0046] track grooves 1 b, 2 b of the outer and inner joint members 1, 2 is defined such that the ratio F/PCR is in the range of 0.069≦F/PCR≦0.121, where the PCR is the length of a line segment between the center O₁of the track groove 1 b of the outer joint member 1 or the center O₂of the track groove 2 b of the inner joint member 2 and the center O₃of the ball 3. Consequently, the allowable load torque, the durability, the maximum operational angle, and the cage strength can be ensured, and also the track load can be decreased. In this embodiment, the ratio F/PCR is defined as F/PCR=0.104 (or 0.1038), which is substantially lower than the typical F/PCR value (i.e., F/PCR=0.14) of the conventional six-ball joint.
As described above, the universal joint of the present embodiment has eight balls. Comparing with the six-ball joint, therefore, the load to be applied on one ball in the universal joint of the present embodiment forms a small portion of the total amount of load. It means that the diameter of each [0047] ball 3 of the present embodiment can be smaller than that of the conventional six-ball joint. FIG. 7 is a partially enlarged cross sectional view of part of the universal joint including the outer joint member 1, the inner joint member 2, and the ball 3. As shown in the figure, the track groove 1 b is axially formed on the inner circumferential surface 1 a of the outer joint member 1, while the track groove 2 b is axially formed on the outer circumferential surface 2 a of the inner joint member 2. Each of these track grooves 1 b, 2 b is shaped like Gothic arch in its lateral cross section.
Thus, the [0048] ball 3 touches the track groove 1 b of the outer joint member 1 at two points C₁₁, C₁₂and also touches the track groove 2 b of the inner joint member 2 at two points C₂₁, C₂₂. Here, a contact angle is defined as an angle α formed by a first line segment passing through the center O₃of the ball 3 and the center O of the joint and a second line segment passing through one of the contact points C₁₁, C₁₂, C₂₁, and C₂₂between the ball 3. As shown in the figure, the contact angles a formed of the line segments between the contact points C₁₁, C₁₂, C₂₁, C₂₂and the center O₃of the ball 3 are equal to each other. In other words, the contact angles a at contact points C₁₁, C₁₂, C₂₁, C₂₂are equal to each other and defined within the range of 29° to 37°. It is noted that the contact angle α (29° to 37°) of the present eight-ball joint is comparatively smaller than the contact angle (37° to 45°) of the conventional six-ball joint.
FIG. 8 is provided for illustrating a wedge angle 2τ of the present universal joint. The wedge angle 2τ is an angle provided for initiating the flip of the wedge in the present universal joint. In other words, the wedge angle is formed by the common normal H[0049] ₁at the contact point C₁between the ball 3 and the track groove 1 b of the outer joint member 1 and the common normal H₂at the contact point C₂between the ball 3 and the track groove 2 b.
As shown in FIG. 8, the contact point C[0050] ₁between the track groove 1 b of the outer joint member 1 and the ball 3 is positioned with an inclination by the curved track groove 1 b at an angle of τ with respect to the center O of the joint passing through the center O₃of the ball 3. Also, the contact point C₂between the track groove 2 b of the inner joint member 2 and the ball 3 is positioned with an inclination by the curved track groove 2 b at an angle of τ with respect to the center O of the joint passing through the center O₃of the ball 3. Therefore, the wedge angle 2τ is provided by adding both angles τ together. If the operational angle of the joint increases, the wedge angle 2τ decreases with a certain phase and finally the wedge can be flipped over.
If the amount of track offset decreases, then the wedge angle 2τ decreases. In this case, however, it allows the [0051] ball 3 to move freely in the ball track at the time of flipping the wedge over, raising the possibility of generating slapping sounds. For avoiding such a possibility, the contact angle α between each of the track grooves 1 b, 2 b and the ball 3 may be defined as 37° or less as described above to set the wedge angle 2τ to at least a normal angle (generally at 9°) or more to be applied in the automobile or the like.

The following table 1 provides a summary of the relationship among the ratio F/PCR, the contact angle α, and the wedge angle 2τ. As described above, F denotes the amount of track offset and PCR denotes the length of a line segment between the center O ₁of the track groove 1 b of the outer joint member 1 or the center O₂of the track groove 2 b of the inner joint member 2 and the center O₃of the ball 3.

TABLE 1


Ratio of offset amount to PCR	Contact angle	Wedge angle
F/PCR	α		2 τ

0.069	45°	8°
	37°	10°
	29°	14°
0.121	45°	14°
	37°	18°
	29°	25°

As is evident from the above table, it is found that the wedge angle 2τ increases as the contact angle α decreases. Also, the wedge angle 2τ increases with an increasing amount of offset F. Therefore, the ratio (F/PCR) of the amount of track offset F and the length of the line segment between the center O[0053] ₁of the track groove 1 b of the outer joint member 1 or the center O₂of the track groove 2 b of the inner joint member 2 and the center O₃of the ball 3 should be set within the range of 0.069≦F/PCR≦0.121 in addition to provide a contact angle α of 37° or less, which is formed by the ball 3 and each of the track grooves 1 b, 2 b. As a result, the contact ellipse between the ball 3 and the track groove 1 b or 2 b becomes difficult to run off the track groove 1 b or 2 b, and substantially no clearance between the ball 3 and the ball track can be found at the contact angle α equal to or less than the normal angle of the automobile or the like. Therefore, the generation of slapping sounds can be prevented.
If the contact angle α formed by the [0054] ball 3 and each of the track grooves 1 b, 2 b decreases, simultaneously the distance from the contact point to the corner (i.e., up to the connection part of the track groove and the inner diameter) increases. As a result, the allowable load torque can be increased. In this case, however, the pressure on the contact surface between the track groove 1 b or 2 b and the ball 3 increases. If the contact angle α is too small, the joint can be resulted in poor durability. Therefore, the contact angle α between the ball 3 and each the track grooves 1 b, 2 b should be defined such that the pressure on the contact surface at the time of loading the basic torque is 2.7 GPa or less. Such a configuration of the universal joint allows the durability which is equal to or more than the durability of the conventional universal joint. According to the present embodiment, the contact angle α between the ball 3 and each of the track grooves 1 b, 2 b of the outer and inner joint members 1, 2 is set to 29° or more, so that the pressure on the contact surface between the track groove 1 b or 2 b and the ball 3 can be suppressed, allowing the same or more excellent durability compared with that of the conventional one.
While there has been described what are at present considered to be preferred embodiments of the invention, it will be understood that various modifications may be made thereto, and it is intended that the appended claims cover all such modifications as fall within the true spirit and scope of the invention. [0055]

Claims

What is claimed is:

1. A constant velocity universal joint, comprising:

an outer joint member having eight curved track grooves axially extending along an inner circumferential surface with a spherical shape;

an inner joint member having eight curved track grooves axially extending along an outer circumferential surface with a spherical shape;

eight balls respectively arranged in eight ball tracks provided as pairs of the track grooves of the outer joint member and the track grooves of the inner joint member; and

a cage having pockets for respectively holding the balls,

a center of each track groove of the outer joint member being axially displaced a predetermined distance from a spherical center of the inner circumferential surface, a center of each track groove of the inner joint member being axially displaced the same distance from a spherical center of the outer circumferential surface in a direction opposite to that of the outer joint member, wherein

a PCD gap in the ball track is in a range of 5 μm to 50 μm.

2. The constant velocity universal joint according to claim 1, wherein

each of the track grooves of the outer joint member and the inner joint member has a bottom with a linear shape provided as a straight portion.

3. The constant velocity universal joint according to claim 1 or claim 2, wherein

a gap between the pocket of the cage and the ball in an axial direction is in a range of −30 μm to +10 μm.

4. The constant velocity universal joint according to claim 1 or claim 2, wherein

a gap between the cage and the outer joint member or the inner joint member in a radial direction is in a range of 20 μm to 100 μm.

5. A constant velocity universal joint, comprising:

a cage having pockets for respectively holding the balls,

a ratio (F/PCR) of an amount (F) of a displacement and a length (PCR) of a line segment between the center of the track groove of the outer joint member or the center of the track groove of the inner joint member and the center of the ball is in a range of 0.069≦F/PCR≦0.121, and

a contact angle of each of the track grooves of the outer joint member and the inner joint member and the corresponding ball is 37° or less.

6. The constant velocity universal joint according to claim 5, wherein

7. The constant velocity universal joint according to claim 5 or claim 6, wherein

the lower limit of the contact angle of each of the track grooves of the outer joint member and the inner joint member and the corresponding ball is defined such that the pressure on the contact surface at the time of loading the basic torque becomes 2.7 Gpa or less.

8. The constant velocity universal joint according to claim 5 or claim 6, wherein

the contact angle of each of the track grooves of the outer joint member and the inner joint member and the corresponding ball is in the range of 29° to 37°.