JPH1113782A - Double Cardan constant velocity joint - Google Patents

Abstract

(57) [Problem] To prevent a large friction between the angle adjusting member 37 and the support plate 26 from being generated even when a large torque is transmitted, and to prevent a significant abrasion. SOLUTION: In order to rotatably support the angle adjusting member 37, a slide bearing 43 is provided at a peripheral portion of a circular hole 32 provided at a central portion of the support plate 26. Even when a large torque is transmitted, metal contact is prevented from occurring at the sliding contact portion between the angle adjusting member 37 and the support plate 26, and significant wear is prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The double cardan type constant velocity joint according to the present invention is incorporated in, for example, a steering device of an automobile, and is used for transmitting a rotational force applied to a steering wheel to a gear box.

[0002]

2. Description of the Related Art A steering apparatus for an automobile is configured to transmit a movement of a steering wheel to a gear box via a steering shaft, a universal joint, and an intermediate shaft so as to impart a desired steering angle to front wheels. . In the case of a general steering device, since the intersection angle (joint angle) between the steering shaft and the intermediate shaft is not large, a general cardan joint (cross-shaped) is used as a universal joint for connecting these two shafts. Universal joint).
As is well known, in a general cardan joint, the transmission of rotational force becomes uneven at a given joint angle, but as long as the joint angle is small, the degree does not pose a practical problem. It has also been practiced to use two cardan joints to counteract unequal speed. However, in recent years, in some automobiles such as cab-over type automobiles, the intersection angle between the steering shaft and the intermediate shaft is often increased in order to improve collision safety. In such a case, if a general cardan joint is used, the non-uniformity of the rotational force transmission becomes so large that it cannot be ignored. Therefore,
In such a case, it is considered to use a double cardan type constant velocity joint.

As a double cardan type constant velocity joint, for example, Japanese Patent Publication No. 50-21610,
What is described in 251746 gazette etc. is conventionally known. Furthermore, by devising the structure of the built-in angle adjusting member, the swing circle is reduced and the installation space is reduced as compared with the double cardan type constant velocity joint described in each of the above publications, and the transmission loss during the transmission of rotational force is reduced. And the structure that can ensure durability,
Some are being studied.

[0004]

DESCRIPTION OF THE PRESENT INVENTION FIGS. 8 to 10 show an example of a double Cardan constant velocity joint incorporating an angle adjusting member 37 whose shape has been devised from such a viewpoint. Note that FIG.
10 to 10 have the same basic configuration as the double cardan constant velocity joint disclosed in Japanese Patent Application Nos. 8-202432 and 8-219676. Double Cardan constant velocity joint 1 shown in FIGS.
Is an intermediate housing 2, first and second yokes 3, 4,
A first cross shaft 5 connecting the first yoke 3 and the intermediate housing 2 is provided, and a second cross shaft 6 connecting the second yoke 4 and the intermediate housing 2 is provided. Intermediate housing 2 of these
Has a pair of first support arms 7, 7 at one axial end (right end in FIGS. 8 to 9) and a pair of second support arms 8, 8 at the other axial end (left end in FIGS. 8 to 9). , Are provided in phase with each other.
Then, first support holes 9, 9 concentric with each other at the distal ends of the first support arms 7, 7, and second support holes 10, 10, 10 concentric with each other at the distal ends of the second support arms 8, 8. Are formed respectively.

The first yoke 3 is provided at one axial end (left end in FIGS. 8 and 9) of a short cylindrical first connecting portion 11 to which an end of a rotating shaft 29 such as a steering shaft can be connected and fixed.
It is provided with a pair of third support arms 12,12. Further, third support holes 13, 13 concentric with each other are formed in the portions of the third support arms 12, 12 near the distal end, respectively. Further, the first connecting portion 11 is provided at an intermediate portion of the first connecting portion 14 for connecting the tips of the third support arms 12 and 12 to each other.
And a first engaging projection 15 projecting to the opposite side.

The second yoke 4 is connected to an end of another rotary shaft (not shown) such as an intermediate shaft or the like at one axial end (FIG. 8 to FIG. Right end of 9)
Is provided with a pair of fourth support arms 17. Then, in the portion near the tip of each of the fourth support arms 17, 17,
Fourth support holes 18, 18 concentric with each other are formed. Further, a second engaging projection 20 is formed at an intermediate portion of the second connecting portion 19 connecting the tips of the fourth support arms 17 and 17 to the opposite side to the second connecting portion 16. ing.

[0007] Of the first and second shaft portions 21 and 22 constituting the first cross shaft 5 in a state orthogonal to each other, both ends of the first shaft portion 21 are formed in the first support holes 9 and 9. on the inside,
Both ends of the second shaft portion 22 are rotatably supported inside the third support holes 13 by radial needle bearings 23, 23, respectively. On the other hand, the third and fourth shaft portions 24 constituting the second cross shaft 6 in a state orthogonal to each other,
25, both ends of the third shaft portion 24 are the second support holes 1
Both ends of the fourth shaft portion 25 are rotatably supported inside the fourth support holes 18 by radial needle bearings 23, 23, respectively.

Further, the intermediate housing 2 has a support plate 26 formed by punching a metal plate such as a steel plate by a press, and punching and bending a metal plate such as a steel plate by a press. And first and second intermediate housing elements 27,28. The first intermediate housing 27 is formed by bending both ends of the flat first substrate portion 30 in the same direction at a right angle to the first substrate portion 30 so that the first support arms 7 are parallel to each other.
7 is assumed. Also, the second intermediate housing element 28
Are bent at both ends of the flat second substrate portion 31 in the same direction and at a right angle to the second substrate portion 31, thereby forming the second support arms 8 and 8 parallel to each other. The support plate 26 and the first and second intermediate housing elements 27, 2
8 is combined with a state in which the support plate 26 is sandwiched between the first and second substrate portions 30 and 31. Then, both the substrate portions 30 and 31 and the support plate 26
Bolts 35, 35 and nuts 36, which are inserted into circular through holes 34, 34 formed in portions where both ends of the
36 and further tightened, the above members 26
28 are fixedly connected to each other.

Further, a circular hole 3 is formed at the center of the support plate 26.
2 is provided at the center of the first and second substrate portions 30 and 31 with circular through holes 33 and 33 having a diameter larger than the circular hole 32.
Are formed respectively. An intermediate portion 38 of the angle adjusting member 37 is rotatably supported inside the circular hole 32. The angle adjusting member 37 includes a cylindrical intermediate portion 38, and first and second crank portions 39, 40 bent from both axial end surfaces of the intermediate portion 38 in the same direction in the diameter direction of the intermediate portion 38. Prepare. The first engagement hole 41 for engaging the first engagement protrusion 15 provided on the first yoke 3 side is formed at the distal end of the first crank portion 39, and the distal end of the second crank portion 40. Engagement hole 42 for engaging the second engagement protrusion 20 provided on the second yoke 4 side with the second engagement hole.
Are formed concentrically with each other. Then, the first engagement projection 15 is inserted into the first engagement hole 41 and the second engagement projection 2
0 are engaged with the second engagement holes 42 so as to be swingable. The inclination angles of the first and second yokes 3 and 4 with respect to the intermediate housing 2 based on the engagement between the first and second engagement protrusions 15 and 20 and the first and second engagement holes 41 and 42. Are matched with each other. In order to enable the intermediate portion 38 to be rotatably supported inside the circular hole 32,
The support plate 26 has a two-part structure in which the support plate 26 is separated at the diameter position of the circular hole 32.

When the first yoke 3 is rotated by the rotation shaft 29 when the double cardan constant velocity joint 1 having the above-described structure is used, the rotation force is applied to the first cross shaft 5 and the intermediate housing. 2. The power is transmitted to the second yoke 4 via the second cross shaft 6. The positional relationship between the first and second yokes 3 and 4 and the intermediate housing 2 changes based on the transmission of the rotational force. This change is caused by the rotation of the angle adjusting member 37 inside the intermediate housing 2. Absorb by things. The angle adjusting member 37 includes:
Although it rotates around the intermediate portion 38, it does not significantly displace in the diameter direction of the intermediate housing 2. That is, only slight movement occurs in the diameter direction due to error absorption. Therefore, the diameter of the intermediate housing 2 is sufficient as long as the rotation of the angle adjusting member 37 is allowed. For this reason, the diameter of the intermediate housing 2 is made smaller than that of the conventional structure described in each of the above publications using a sliding plate type angle adjusting member, and the swing circle of the double cardan type constant velocity joint 1 is formed. And the installation space can be reduced. Further, since the force required to rotate the angle adjusting member 37 is small, the power transmission loss at the double cardan constant velocity joint 1 is small.

[0011]

In the case of the double cardan constant velocity joint 1, when the torque to be transmitted increases, the sliding contact between the angle adjusting member 37 and the support plate 26 may be significantly worn. That is, the inner peripheral edge of the circular hole 32 formed at the center of the support plate 26 and the peripheral portion of the circular hole 32 at the center of both sides of the support plate 26 are in sliding contact with the intermediate portion 38 of the angle adjusting member 37. When the torque increases, the surface pressure applied to the sliding contact portion increases, the oil film of the portion breaks, and the metal forming the support plate 26 and the metal forming the angle adjusting member 37 come into direct contact with each other, so-called metal contact. Occurs. When such metal contact occurs, the wear of the sliding contact portion becomes remarkable, and the durability of the double cardan constant velocity joint is impaired.

If one of the support plate 26 and the angle adjusting member 37 is made of a self-lubricating metal such as copper, or an oil-impregnated metal or a synthetic resin having a low friction coefficient, the remarkable wear described above is prevented. it can. However, these materials are more expensive than steel (in the case of copper and oil-impregnated metal), have low rigidity (in the case of copper and synthetic resin), and have poor toughness (in the case of oil-impregnated metal) )
Depending on the application of the double cardan type constant velocity joint, it cannot be adopted, and both the support plate 26 and the angle adjusting member 37 must be made of steel. In order to prevent the abrasion, a coating layer made of a low friction material such as polytetrafluoroethylene (PTFE) or molybdenum disulfide may be formed on the surface of the support plate 26.
However, even when the coating layer is formed, if the torque to be transmitted is large, the effect of preventing wear for a long period of time may not be sufficient. The double cardan constant velocity joint of the present invention has been invented in view of such circumstances.

[0013]

A double cardan type constant velocity joint according to the present invention comprises an intermediate housing, a first and second yoke, and a first and second yoke, similarly to a conventionally known double cardan type constant velocity joint. A first cross shaft connecting the yoke and the intermediate housing; and a second cross shaft connecting the second yoke and the intermediate housing. The intermediate housing is provided with a pair of first support arms at one end in the axial direction and a pair of second support arms at the other end in the axial direction in the same phase. And a second support hole concentric with each other is formed at the tip of each of the second support arms. The first yoke is provided with a pair of third support arms at one end in the axial direction of the first connection portion capable of connecting and fixing the ends of the rotating shaft, and the first support portions are concentric with each other near the tip of each of the third support arms. The third support hole is formed respectively, and furthermore, a first engagement protrusion protruding on the opposite side to the first connection portion is provided at an intermediate portion of the first connection portion connecting the tips of the third support arms. It is formed. The second yoke is provided with a pair of fourth support arms at one end in the axial direction of a second connecting portion capable of connecting and fixing an end of another rotating shaft, and a portion near the tip of each of the fourth supporting arms. Fourth support holes concentric with each other are formed, and a second engagement protrusion protruding on the opposite side to the second connection portion is provided at an intermediate portion of a second connection portion connecting the tips of the fourth support arms. A part is formed. Further, among the first and second shaft portions constituting the first cross shaft in a state orthogonal to each other, both end portions of the first shaft portion are rotatably supported inside the first support hole, and Both ends of the biaxial portion are rotatably supported inside the third support hole. Further, among the third and fourth shaft portions constituting the second cross shaft in a state orthogonal to each other, both end portions of the third shaft portion are rotatably supported inside the second support hole, Both ends of the four shafts are rotatably supported inside the fourth support hole. Further, an angle adjusting member that is displaceable with respect to the intermediate housing is provided at an axial intermediate portion of the intermediate housing, and first and second engaging holes are formed at both axial end portions of the angle adjusting member. ,
They are formed in phase with each other. The first engagement projection is engaged with the first engagement hole, and the second engagement projection is engaged with the second engagement hole so as to be swingably displaceable. The inclination angles of the first and second yokes are matched with each other.

In particular, in the double cardan type constant velocity joint of the present invention, a support plate provided at an axially intermediate portion of the intermediate housing, a circular hole formed at the center of the support plate, The crank-type angle adjusting member has an intermediate portion rotatably supported inside the circular hole. Of these, the angle adjusting member is a cylindrical intermediate part,
First and second crank portions are bent from both axial end surfaces of the intermediate portion in the same diametric direction of the intermediate portion. The first engagement hole is formed at the tip of the first crank portion, and the second engagement hole is formed at the tip of the second crank portion. In addition, a sliding bearing made of a low-friction material is added to a portion of the support plate that slides in contact with a part of the angle adjusting member at both sides of the central portion and at the inner peripheral edge of the circular hole, and a metal forming the support plate is provided. And the metal constituting the angle adjusting member are prevented from directly rubbing each other.

[0015]

The operation of transmitting the rotational force between the first yoke and the second yoke while maintaining constant velocity by the double cardan constant velocity joint of the present invention configured as described above is as follows.
This is the same as the double cardan type constant velocity joint shown in FIGS. Particularly, in the case of the double cardan constant velocity joint of the present invention, the metal forming the support plate and the metal forming the angle adjusting member do not directly rub against each other due to the existence of the slide bearing. For this reason, even when the torque to be transmitted is large, no significant wear occurs at the sliding contact portion between the support plate and the angle adjusting member.

[0016]

1 to 6 show an embodiment of the present invention. The feature of the present invention is to prevent abrasion of a sliding portion between the angle adjusting member 37 and the support plate 26.
The structure of the portion where the slide bearing 43 is mounted on the support plate 26 is provided. Since the structure and operation of the other parts are the same as the structure according to the preceding invention shown in FIGS. 8 to 10 above, the description of the equivalent parts will be omitted or simplified, and the characteristic parts of the present invention will be described below. In addition, a description will be given focusing on a new structure part which has not been described in the part describing the structure shown in FIGS.

Each of the support plates 26 is shown in FIG.
By combining a pair of half pieces 44, 44 having a shape as shown in FIG. 5, the whole is formed in a ring shape. Each of the halves 44, 44 is formed in a semicircular arc shape, and the protrusion 45 is fitted to one end in the circumferential direction and the protrusion 45 is fitted to the other end in the circumferential direction without play. The recess 46
Each is formed. In the illustrated example, the protruding piece 45 and the concave part 46 each having a trapezoidal shape are formed at the center of the circumferential edge. As shown in FIG. 5, both ends of the pair of halves 44, 44 in the circumferential direction are opposed to each other, and a protrusion 45 formed on the circumferential end of the halves 44, 44 and the recess 46 are fitted. The two halves 44 are combined concentrically with each other to form the annular support plate 26.

A thin portion 47 is formed on the inner peripheral edge of each of the halves 44 constituting the support plate 26 by plastic working such as coining or cutting such as milling. The thin portion 47 is formed by the halves 44, 4
4 exists in the center with respect to the thickness direction. Therefore, annular concave portions 48, 48 are formed around the entire circumference at the center of both surfaces of the support plate 26, which is formed by combining the pair of halves 44, 44, in the shape of a circular ring, around the circular hole 32. Exists.

A slide bearing 43 as shown in FIG. 4 is additionally provided at the peripheral portion of the circular hole 32 surrounded by the recesses 48, 48 as described above. The entire sliding bearing 43 is formed in a ring shape by combining a pair of bearing elements 49, 49 divided into two in the diameter direction. Each of the bearing elements 49 and 49 is made of a polyamide resin, a polyacetal resin alone or a mixture of an antiwear agent and a friction reducing agent, and a synthetic material having excellent wear resistance and lubricity, such as polytetrafluoroethylene resin. It is formed of a lubricating metal material such as resin, copper, oil-impregnated metal, etc., and is formed in a semicircular arc shape with a U-shaped cross section that is open outward in the diameter direction. Each of these bearing elements 49, 49 has a flat plate portion 50,
50, and an arc-shaped plate portion 51 that connects the inner peripheral edges of the two flat plate portions 50, 50 to each other. Of these, the outer diameter D50 of the two flat plate portions 50, ₅₀
8 the same as the outer diameter D ₄₈ of, and slightly smaller (D ₅₀ ≦ D ₄₈₎ than the outer diameter D _48. The outer diameter D ₅₁ of the arcuate plate portion 51 is equal to or inside diameter R ₃₂ of the circular hole 32 is slightly smaller (D ₅₁ ≦ R ₃₂₎ than the inner diameter R _32.

Therefore, the sliding bearing 43 formed by combining the bearing elements 49, 49 can be mounted on the peripheral portion of the circular hole 32 provided at the center of the support plate 26 with almost no play. With the sliding bearing 43 attached to the center of the support plate 26 in this manner, the flat plates 50, 50 fit in the recesses 48, 48, respectively.
The projection 50 does not protrude from both sides of the support plate 26, or does not enter from both sides. However, each of the flat portions 50,
The outer diameter D ₅₀ of 50, in the case of the swing circle of angular alignment member 37 diameter (angular alignment member 37 is rotated about the intermediate portion 38, the first, second double crank portion 39,
(The diameter of the trajectory of the leading edge of the support plate 40), it is not necessary to make the outer surfaces of the flat plates 50, 50 coincide exactly with both surfaces of the support plate 26. For example, each recess 4
8 and 48 are omitted, and the outer surfaces of the flat plate portions 50 and 50 are placed on both sides of the support plate 26 so that the flat plate portions 50 and 50 are
May be protruded by the thickness of the plate. It should be noted that if the corrugated bulges 54, 54 as shown in FIG. 6 are formed in a part of the flat plates 50, 50 of each of the bearing elements 49, 49 constituting the sliding bearing 43, , 50 are sandwiched between the thin portion 47 and the first and second crank portions 39, 40, and the bulging portions 54, 54 are elastically compressed, so that each of the bearing elements 4
It is possible to more reliably prevent rattling of 9, 49.

In the case of the double cardan type constant velocity joint of the present invention configured as described above, the pair of bearing elements 4
Due to the existence of the slide bearings 43 composed of 9 and 49, the metal such as steel constituting the support plate 26 does not directly rub against the metal such as steel constituting the angle adjusting member 37. For this reason, even when the torque to be transmitted is large and the angle adjusting member 37 is strongly pressed against the support plate 26, significant wear occurs at the sliding contact portion between the support plate 26 and the angle adjusting member 37. Absent. Preferably,
In order to prevent the slide bearing 43 from rotating with respect to the support plate 26, the rotation of the slide bearing 43 is prevented between one or both of the pair of bearing elements 49, 49 and the support plate 26. A concave and convex engaging portion for achieving the above is provided. As a portion provided with such an uneven engagement portion, for example, the arc plate portion 51
And the inner peripheral edge of the circular hole 32 are aligned with each other.

Further, in the illustrated example, projecting pieces 45 are provided on both circumferential edges of each of the half pieces 44, 44 constituting the support plate 26.
When the support plate 26 is formed by combining a pair of half pieces 44, 44, these protrusions 45 are formed.
And the recess 46 are engaged with each other. Therefore, the assemblability of the support plate 26 can be improved and the assembling accuracy can be ensured. That is, for the purpose of cost reduction, each half 4
When making 4, 44 by punching steel plate,
On the periphery of each of these halves 44, a shear surface 52 and a fracture surface 53 are formed as shown in FIG. Among them, the shear surface 52 has stable dimensional accuracy and shape accuracy, but the accuracy of the fracture surface 53 is poor. Therefore, the pair of halves 44,
When the support plate 26 is configured by combining the
It is necessary to abut the shear surfaces 52 (without abutting the shear surface 52 and the fracture surface 53) to obtain the support plate 26 having a desired accuracy.

As shown in the example of the drawing, both ends in the circumferential direction of a pair of halves 44, 44 each having a shape as shown in FIGS. If the protruding piece 45 and the concave portion 46 formed on the edge in the direction are fitted to each other to form the annular support plate 26, the sheared surfaces 52 can be connected to each other (without abutting the sheared surface 52 and the fractured surface 53). The supporting plates 26 having the desired accuracy can be obtained by butting. Since this work can be reliably performed simply by fitting the protruding piece 45 and the concave part 46, the work of combining the pair of halves 44, 44 can be easily performed. In addition, the fitting portion between the protruding piece 45 and the concave portion 46 prevents the pair of halves 44, 44 constituting the support plate 26 from moving in the circumferential direction after the combination, and Stiffness of the double cardan constant velocity joint incorporating the support plate 26 is also ensured. On the contrary,
When the circumferential ends of the halves 44, 44 are simply formed in a straight line, any one of the operation of abutting the sheared surfaces 52 and the operation of concentrically combining the pair of halves 44, 44 can be used. Also becomes troublesome. Even when the projecting piece 45 and the concave part 46 are formed, since the pair of half pieces 44, 44 use the same kind of parts obtained by punching a steel plate by pressing, The cost of the plate 26 can be reduced.

[0024]

According to the present invention, since the present invention is constructed and operated as described above, there is no occurrence of remarkable wear even when transmitting a large torque, and a double cardan type constant velocity joint having excellent durability is provided. realizable.

[Brief description of the drawings]

FIG. 1 is a partially cut-away side view showing an example of an embodiment of the present invention.

FIG. 2 is a partially cut-away side view showing a state rotated 90 degrees from the state of FIG. 1;

3A and 3B show a half of a supporting plate, and FIG. 3A shows a state before machining a concave portion for adding a slide bearing;
(B) is a perspective view showing the state after processing, respectively.

FIG. 4 is an exploded perspective view of the slide bearing.

FIG. 5 is a front view showing a pair of halves forming a support plate.

FIG. 6 is a view similar to FIG. 4, showing another example of the slide bearing.

FIG. 7 is an enlarged sectional view taken along the line AA of FIG. 5;

FIG. 8 is a partially cut-away side view showing a structure according to the prior invention as a premise of the present invention.

FIG. 9 shows a state in which the first and second yokes are moved from the state shown in FIG.
FIG. 4 is a partially cut side view showing the state rotated by degrees.

FIG. 10 is a perspective view of an angle adjusting member.

[Explanation of symbols]

 Reference Signs List 1 double cardan constant velocity joint 2 intermediate housing 3 first yoke 4 second yoke 5 first cross shaft 6 second cross shaft 7 first support arm 8 second support arm 9 first support hole 10 second support hole 11th One connecting part 12 Third supporting arm 13 Third supporting hole 14 First connecting part 15 First engaging projection 16 Second connecting part 17 Fourth supporting arm 18 Fourth supporting hole 19 Second connecting part 20 Second engaging Projection 21 First shaft portion 22 Second shaft portion 23 Radial needle bearing 24 Third shaft portion 25 Fourth shaft portion 26 Support plate 27 First intermediate housing element 28 Second intermediate housing element 29 Rotating shaft 30 First substrate portion 31 Second substrate portion 32 Circular hole 33 Through hole 34 Through hole 35 Bolt 36 Nut 37 Angle adjusting member 38 Intermediate portion 39 First crank portion 40 Second crank portion 41 First engagement hole 42 Second engagement hole 43 Slide bearing 44 half piece 45 protruding piece 46 concave part 47 thin part 48 concave part 49 bearing element 50 flat plate part 51 arc plate part 52 shear plane 53 fracture plane 54 bulging part

Claims (1)

[Claims] An intermediate housing, a first and a second yoke, a first cross shaft connecting the first yoke and the intermediate housing, and a second cross shaft connecting the second yoke and the intermediate housing. The intermediate housing is provided with a pair of first support arms at one end in the axial direction and a pair of second support arms at the other end in the axial direction, respectively, in the same phase. A first support hole concentric with each other, and a second support hole concentric with each other at a distal end of each of the second support arms, respectively, and the first yoke is capable of connecting and fixing an end of a rotating shaft. A pair of third support arms are provided at one end in the axial direction of the first coupling portion, and third support holes concentric with each other are formed in portions near the ends of the third support arms. Protrudes in the middle of the first connecting part connecting the tips of The second yoke is provided with a pair of fourth support arms at one end in the axial direction of a second connecting portion capable of connecting and fixing an end of another rotating shaft. A fourth support hole concentric with each other is formed in a portion near the tip of each of the fourth support arms, and the second connection portion is connected to an intermediate portion of a second connection portion connecting the tips of the fourth support arms. Forming a second engaging projection projecting to the opposite side to the part, the first and the second cross-shaft constituting the first cross axis in a state orthogonal to each other.
Of the second shaft, both ends of the first shaft are rotatably supported inside the first support hole, and both ends of the second shaft are freely rotatable inside the third support hole. Third, which constitutes the second cross axis in a state orthogonal to each other,
Of the fourth shaft, both ends of the third shaft are rotatably supported inside the second support hole, and both ends of the fourth shaft are freely rotatable inside the fourth support hole. The intermediate housing is provided with an angle adjusting member which is displaceable with respect to the intermediate housing at an axially intermediate portion, and first and second engaging members are provided at both axial ends of the angle adjusting member. The mating holes are formed in the same phase with each other, and the first engaging protrusion is swingably displaceable to the first engaging hole, and the second engaging protrusion is swingable to the second engaging hole. In the double cardan type constant velocity joint in which the inclination angles of the first and second yokes with respect to the intermediate housing are matched with each other, a support plate provided at an intermediate portion in the axial direction of the intermediate housing is provided. A circular hole formed in the center of the support plate, A crank-type angle adjusting member rotatably supported at the intermediate portion, wherein the angle adjusting member has a cylindrical intermediate portion and a diametrical direction of the intermediate portion from both axial end surfaces of the intermediate portion. The first engagement hole is formed at the distal end of the first crank portion, and the second engagement hole is formed at the distal end of the second crank portion, respectively. A sliding bearing made of a low-friction material is attached to a portion of the support plate that slides in contact with a part of the angle adjusting member at both sides of the center of the support plate and at the inner peripheral edge of the circular hole to constitute the support plate. A double cardan constant velocity joint characterized in that the metal to be formed and the metal constituting the angle adjusting member are prevented from directly rubbing each other.