JP2009168190A - Double cardan joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a double Cardan joint having an excellent constant velocity property which is not affected by variations of a joint angle between an input shaft and an output shaft. <P>SOLUTION: In the double Cardan joint having a socket york 11, a pin york 12, a coupling york 13, cross bearings 14, 15, and a spherical roller bearing 16 housed in the socket york 11 and combining the socket york 11 and the pin york 12 at a bending-free state, the socket york 11 has a cylindrical section 33 for sliding the spherical roller bearing 16 in the axial direction of the socket york 11. The coupling york 13 has first and second spherical roller bearing guides 47, 48 for sliding the spherical roller bearing 16 in a direction orthogonal to the axial direction of the coupling york 13. The pin york 12 has a cylinder section 37 for sliding in a through-hole 16a formed on the spherical roller bearing 16. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a double cardan joint, and more particularly to a double cardan joint in which the angular velocities of an input shaft and an output shaft are made equal even when the joint angle formed between the input shaft and the output shaft changes.

  Conventionally, as this type of double cardan joint, for example, as shown in FIG. 11A, a socket yoke 101 as a first yoke and a pin yoke 102 as a third yoke are used as a second yoke. There is known a double cardan joint 100 that is flexibly connected via a coupling yoke (not shown) and cross bearings 103 and 104 serving as cross shafts (see, for example, Patent Document 1).

  In the double cardan joint 100, a spherical bearing 105a and a spherical bearing sheet 105b constituting the spherical bearing 105 are interposed between a cylindrical portion 101a provided on the socket yoke 101 and a pin 102a provided on the pin yoke 102. Yes. The spherical bearing 105 a is rotatably supported with respect to the pin 102 a of the pin yoke 102 via a needle bearing (not shown), and the spherical bearing sheet 105 b is fixed to the inner peripheral portion of the cylindrical portion 101 a of the socket yoke 101. Thus, the spherical bearing 105a and the spherical bearing sheet 105b slide.

  In this case, for example, the socket yoke 101 is connected to an input shaft (not shown), the pin yoke 102 (not shown) is connected to the output shaft, and the input shaft and the output shaft are bent around the center Pb of the spherical bearing 105a. It has become. Since the pin 102a of the pin yoke 102 slides in the axial direction in the spherical bearing 105a, even if the joint angle formed by the input shaft and the output shaft changes, compared with a cardan joint composed of a single cross bearing, The rotation of the input shaft is transmitted to the output shaft at a substantially constant speed.

JP 2000-291680 A

In conventional double Cardan joint 100 described above, as shown in FIG. 11 (a), the rotation center _{P 1} and rotation straight line L connecting the rotation center _{P 2} of Pin'yoku 102 center _{P 1} and spherical bearing 105a of the socket yoke 101 central Pb and the angle theta is the straight line [Delta] L ₁ connecting, when the straight line L and the rotation center P ₂ and the straight line [Delta] L ₂ and the angle theta ₂ connecting the center Pb of the spherical bearing 105a are equal, i.e., [Delta] L of ₁ is equal to the distance ΔL ₂ , the angular velocity ω ₁ (rad / s) of the socket yoke 101 is equal to the angular velocity ω ₂ (rad / s) of the pin yoke 102, and the socket yoke 101 and the pin yoke 102 Rotates at a constant speed. Here, the angular velocity represents the speed of rotation of the object. For example, the angular velocity represents the time change of the angle θ in the polar coordinates represented by the radius r and the angle θ from the reference, and represents the angle advanced per unit time. . Therefore, the angular velocity does not change if the circular motion is constant.

However, as shown in FIG. 11B, when the swing of the socket yoke 101 and the pin yoke 102 is large, the angle θ ₁ ′ formed by the straight line L and the straight line ΔL ₁ , the straight line L and the straight line ΔL ₂ , And the angle θ ₂ ′ formed by θ ₁ ′> θ ₂ ′. That is, the distance ΔL ₁ and the distance ΔL ₂ ′ are not equal because ΔL ₂ ′> ΔL ₁ .

FIG. 10 illustrates a joint angle (deg) formed by any one of the input shaft and the output shaft and the straight line L, for example, an angle θ ₂ to θ ₂ ′ formed, and an angular velocity (rad) of any of the input shaft and the output shaft. / S), that is, a graph showing the relationship with the time change of the angle θ in polar coordinates.
The bent line shown in FIG. 10 shows the change in the angular velocity on the output shaft side in the prior art. In the case of this bent line, when the joint angle formed by the axis on the output shaft side and the straight line L is 0 deg and θa, the angle θ ₁ and the angle θ ₂ shown in FIG. And the output shaft becomes constant speed. However, at other angles, the angle θ ₁ and the angle θ ₂ are not equal, and the angular velocity changes.

As a result, the angular velocity ω ₁ of the socket yoke 101 and the angular velocity ω _{2 of the} pin yoke 102 are not equal, and the socket yoke 101 and the pin yoke 102 rotate at unequal speed, so that vibration is excited in the double cardan joint 100. There was a risk of noise. In addition, the efficiency of torque transmission may be reduced. As described above, the conventional double cardan joint 100 has a problem that the constant velocity is insufficient.

  The present invention has been made to solve the above-described conventional problems, and provides a double cardan joint having excellent constant velocity that is not affected by a change in joint angle between an input shaft and an output shaft. Objective.

  In order to achieve the above object, the double cardan joint according to the present invention is (1) a second connected to the first yoke via a first yoke and a first cross shaft having two axes orthogonal to each other. A yoke, a third yoke coupled to the second yoke via a second cross shaft having two axes orthogonal to each other, and the first yoke housed in the first yoke, In a double cardan joint provided with a spherical bearing that flexibly couples with the third yoke, the first yoke has a cylindrical portion that slides the spherical bearing in the axial direction of the first yoke. And the second yoke has a bearing guide member that slides the spherical bearing in a direction orthogonal to the axial direction of the second yoke, and the third yoke is formed on the spherical bearing. Has a cylindrical part that slides in the through hole It is characterized in.

  With this configuration, the spherical bearing slides in the axial direction of the first yoke in the cylindrical portion of the first yoke, and the cylindrical portion of the third yoke slides in the through hole formed in the spherical bearing. Since it moved, the spherical bearing can be slid in the direction orthogonal to the axial direction of the second yoke by the bearing guide member of the second yoke. As a result, since the movement of the spherical bearing is regulated in the sliding direction by the bearing guide member, when the first yoke and the third yoke are bent through the spherical bearing, the center of the spherical bearing and the first yoke are The angle between the straight line connecting the rotation center of the first yoke and the straight line connecting the rotation center of the first yoke and the rotation center of the third yoke, and the rotation center of the spherical bearing and the third yoke. Is equal to the angle formed by the straight line connecting the rotation center of the first yoke and the rotation center of the third yoke. As a result, the first yoke and the third yoke rotate at a constant speed. For example, the joint angle between the input shaft connected to the first yoke and the output shaft connected to the third yoke is Even if it changes, excellent constant velocity can always be obtained.

  In the double cardan joint described in (1), preferably, (2) the bearing guide member of the second yoke sandwiches the spherical bearing with the first spherical bearing guide for guiding the spherical bearing. The second spherical bearing guide is arranged opposite to the first spherical bearing guide and guides the spherical bearing.

  With this configuration, the spherical bearing can be reliably slid in the direction perpendicular to the axial direction of the second yoke by the first spherical bearing guide and the second spherical bearing guide.

  In the double cardan joint according to the above (1) or (2), preferably, (3) the second yoke includes first pressing means for pressing the spherical bearing by the first spherical bearing guide. And a second pressing means for pressing the spherical bearing by the second spherical bearing guide.

  With this configuration, the first spherical bearing guide and the second spherical bearing guide ensure that the spherical bearing slides in a direction orthogonal to the axial direction of the second yoke, and the spherical bearing is the first spherical bearing guide and Vibration generated in the second spherical bearing guide can be suppressed, and noise is reduced.

  In the double cardan joint according to the above (1) to (3), (4) the first yoke is formed by the bearing guide member in a direction orthogonal to the direction in which the spherical bearing slides. A second through hole formed to slide the first spherical bearing guide in the first through hole and to face the first through hole across the spherical bearing. It is preferable to have a through-hole and slide the second spherical bearing guide in the second through-hole.

  With this configuration, the spherical bearing can be moved in a direction orthogonal to the direction of sliding with the bearing guide member, and the first yoke and the third yoke are in a direction orthogonal to the direction of sliding with the bearing guide member. Even when it swings, a straight line connecting the center of the spherical bearing and the rotation center of the first yoke and a straight line connecting the rotation center of the first yoke and the rotation center of the third yoke are formed. The angle formed by the straight line connecting the center of the spherical bearing and the rotation center of the third yoke and the straight line connecting the rotation center of the first yoke and the rotation center of the third yoke is equal. Become. As a result, the first yoke and the third yoke rotate at a constant speed. For example, the joint angle between the input shaft connected to the first yoke and the output shaft connected to the third yoke is Even if it changes, excellent constant velocity can always be obtained.

  In the double cardan joint described in the above (1) to (4), preferably, (5) the first pressing means is configured by a first leaf spring having a bent portion, and the first leaf spring. One end of the second plate spring is fixed to the side surface of the first spherical bearing guide, the second pressing means is constituted by a second leaf spring having a bent portion, and one end of the second leaf spring is the second leaf spring. The spherical bearing guide is configured to be fixed to the side surface.

  With this configuration, the first leaf spring fixed to the first spherical bearing guide 47 when the spherical bearing moves and the first spherical bearing guide and the second spherical bearing guide slide in the through hole. Contracts. On the other hand, since the second leaf spring fixed to the second spherical bearing guide expands, the spherical bearing reliably contacts the first spherical bearing guide regardless of the magnitude of the movement, and the second spherical bearing. Secure contact with the guide. When the spherical bearing tries to return to the original position, the first and second leaf springs can reliably return the spherical bearing to the original position.

  ADVANTAGE OF THE INVENTION According to this invention, the double cardan joint which has the outstanding constant velocity property which is not influenced by the change of the joint angle of an input shaft and an output shaft can be provided.

  Embodiments of the present invention will be described below with reference to the drawings.

(Embodiment)
FIG. 1 is a plan view of a propeller shaft 1 to which a double cardan joint 10 according to a first embodiment of the present invention is applied, FIG. 2 is a plan view of the double cardan joint 10, and FIG. 4 is a side view of the double cardan joint 10, FIG. 4 is a cross-sectional view showing the AA cross section of FIG. 3, FIG. 5 is a cross-sectional view showing the BB cross section of FIG. 3, and FIG. It is sectional drawing which shows CC cross section of FIG.

First, the configuration will be described.
The double cardan joint 10 is mounted on a vehicle and constitutes a part of the propeller shaft 1 as a propulsion shaft. The vehicle is a large automobile, an ordinary automobile, or the like, and is configured by an ordinary automobile equipped with an internal combustion engine such as a 4-cylinder gasoline engine or a diesel engine.

  As shown in FIG. 1, the propeller shaft 1 includes a so-called biaxial three-joint. The first joint 2, the first propeller shaft 3 connected to the first joint 2, and the first Double cardan joint 10 connected to propeller shaft 3, second propeller shaft 4 connected to double cardan joint 10, third joint 5 connected to second propeller shaft 4, and first propeller A center bearing 6 that supports the shaft 3 is included.

  The first joint 2 is composed of a shaft joint that connects two intersecting axes and transmits a rotational force, and is composed of, for example, a universal joint such as a hook-type universal joint or a constant velocity universal joint. Similarly to the first joint 2, the third joint 5 is also composed of a universal joint such as a hook-type universal joint and a constant velocity universal joint.

  As shown in FIG. 2, the double cardan joint 10 includes a socket yoke 11 as a first yoke, a pin yoke 12 as a third yoke, a coupling yoke 13 as a second yoke, and a socket yoke 11. A cross bearing 14 as a first cross shaft to be attached, a cross bearing 15 as a second cross shaft to be attached to the pin yoke 12, a spherical bearing 16 to be inserted into the socket yoke 11 shown in FIG. A needle bearing 17 mounted in the bearing 16 and a retainer 18 that holds the needle bearing 17 are configured.

As shown in FIGS. 2 to 4, the socket yoke 11 includes a flange portion 31, a main body portion 32, and a tubular portion 33. The first propeller shaft 3 is connected to the flange portion 31 by fastening means such as a bolt (not shown). A through hole 32a is formed in the main body 32 in a direction orthogonal to the axial direction, and the axis of the through hole 32b is formed on the side facing the through hole 32a so as to coincide with the axis of the through hole 32a. In addition, both end portions of the cross bearing 14 in the direction of the axis line JA ₁₁ are inserted into the through holes 32 a and 32 b, respectively, so that the socket yoke 11 can rotate around the axis line JA ₁₁ of the cross bearing 14.

  The cylindrical portion 33 is formed so as to protrude from one end portion in the axial direction of the main body portion 32 so that the axis line of the main body portion 32 and the axial line of the cylindrical portion 33 coincide with each other. The guide 33a and the second guide 33b facing each other.

  As shown in FIG. 5, a groove 33 c formed of a curved surface having a radius substantially the same as the radius of the spherical bearing 16 is formed in the radial direction of the first guide 33 a in the axial direction of the cylindrical portion 33. A groove 33d formed of a curved surface having a radius substantially the same as the radius of the spherical bearing 16 is also formed in the axial direction of the cylindrical portion 33 on the radially inner side of the second guide 33b. . The spherical bearing 16 is interposed between the groove 33c of the first guide 33a and the groove 33c of the second guide 33b, and is guided by the groove 33c and the groove 33d so as to slide in the cylindrical portion 33. It has become.

  A chamfer 33e is formed at the tip of the first guide 33a so that it does not interfere with the pin yoke 12 when the socket yoke 11 rotates. A chamfer 32f is also formed at the tip of the second guide 33b so that it does not interfere with the pin yoke 12 when the socket yoke 11 rotates.

The pin yoke 12 includes a main body portion 36 and a cylindrical portion 37. The second propeller shaft 4 is connected to one end of the main body 36 in the axial direction. A through hole 36a is formed in the main body 36 in a direction perpendicular to the axial direction, and a through hole 36b is formed on the side facing the through hole 36a so as to coincide with the axis of the through hole 36a. Both end portions of the cross bearing 15 in the direction of the axis JA ₁₂ are inserted into the through holes 36a and 36b, respectively, so that the pin yoke 12 can rotate around the axis JA ₁₂ of the cross bearing 15.
The cylindrical portion 37 has a circular cross section, and is formed to protrude from the other end portion 36 c in the axial direction so that the axis of the main body 36 and the axis of the cylindrical portion 37 coincide with each other, and is inserted into the spherical bearing 16. It has become so.

  As shown in FIGS. 4 and 5, the spherical bearing 16 is formed of a sphere having a predetermined radius, and a through hole 16a is formed so as to penetrate the axis of the sphere so as to intersect with the center of the sphere. A needle bearing 17 is inserted into the through hole 16 a, and the needle bearing 17 is held in the spherical bearing 16 by a retainer 18. Further, the cylindrical portion 37 of the pin yoke 12 is inserted into the needle bearing 17 so that it can rotate within the spherical bearing 16.

  As described above, when the joint angle between the socket yoke 11 and the pin yoke 12 is relatively 0, the axis of the socket yoke 11 and the axis of the pin yoke 12 are configured to coincide with each other via the spherical bearing 16. .

  As shown in FIG. 2, the coupling yoke 13 includes a main body portion 41 formed in a cylindrical shape, and a flange that is integrally formed with the main body portion 41 extending from one end portion in the axial direction of the main body portion 41. It includes a portion 42 and a flange portion 43 formed so as to face the flange portion 42 with the main body portion 41 interposed therebetween. Further, as shown in FIG. 3, it includes a flange portion 44 and a flange portion 45 formed so as to face the flange portion 42 and the flange portion 43, respectively, across the axis of the coupling yoke 13.

As shown in FIGS. 5 and 6, the body portion 41 is formed with a through hole 41 a having a rectangular cross section with a width W ₁ and a length W ₂ in a direction orthogonal to the axial direction thereof. A through hole 41b having the same cross section as the through hole 41a is formed on the side facing 41a.
A first spherical bearing guide 47 is inserted into the through hole 41a. The first spherical bearing guide 47 has a slightly smaller width than the width W _1, a rectangular cross section of length W ₂ slightly less than the length, so that the slidable in the through hole 41a . Further, the tip of the first spherical bearing guide 47 is formed with an arc surface 47 a having a radius substantially the same as the radius of the spherical bearing 16, and holds the spherical bearing 16.

A second spherical bearing guide 48 is inserted into the through hole 41b. Second spherical bearing guide 48, like the first spherical bearing guide 47 has a slightly smaller width than the width W _1, a rectangular cross section of length W ₂ slightly less than the length, the through-hole It can slide within 41b. Further, similarly to the first spherical bearing guide 47, an arc surface 48a having a radius substantially the same as the radius of the spherical bearing 16 is formed at the distal end portion of the second spherical bearing guide 48. It comes to hold.

  As shown in FIGS. 4 and 6, a first leaf spring 51 bent in an arc shape is fixed to a side surface 47b in the vicinity of one end of the first spherical bearing guide 47, and the first spherical bearing guide 47 A first leaf spring 61 having the same shape as the first leaf spring 51 is fixed to a side surface 47 b in the vicinity of the other end of 47. Further, a leaf spring 52 bent in an arc shape is fixed to a side surface 47 c near one end of the first spherical bearing guide 47, and a side surface 47 c near the other end of the first spherical bearing guide 47 is fixed. A first leaf spring 62 having the same shape as the first leaf spring 51 is fixed. The first spherical bearing guide 47 presses the spherical bearing 16 radially inward by the first leaf springs 51, 52, 61, 62.

  A second leaf spring 53 bent in an arc shape is fixed to a side surface 48 b near one end of the second spherical bearing guide 48, and is attached to a side surface 48 b near the other end of the second spherical bearing guide 48. A second leaf spring having the same shape as the first leaf spring 51 is fixed. A second leaf spring 54 bent in an arc shape is fixed to a side surface 47 c in the vicinity of one end of the second spherical bearing guide 48, and a side surface in the vicinity of the other end of the second spherical bearing guide 48. A second leaf spring having the same shape as the first leaf spring 51 is fixed to 48c. Similarly to the first spherical bearing guide 47, the second spherical bearing guide 48 also presses the spherical bearing 16 radially inward by the second leaf springs 53 and 54 and two second leaf springs (not shown). is doing.

And the distal end portion of the first spherical bearing guide 47, the distance L ₂ between the tip portion of the second spherical bearing guide 48, than the width L ₁ of the first guide 33a and second guide 33b of the cylindrical portion 33 The spherical bearing 16 is slidably guided by the arc surface 47a of the first spherical bearing guide 47 and the arc surface 48a of the second spherical bearing guide 48.

As shown in FIG. 6, a through hole 42 a is formed in the flange portion 42 in a direction orthogonal to the axial direction thereof, and a through hole 44 a is formed in the flange portion 44 on the side facing the through hole 42 a. It is formed so as to match with the axis of the hole 42a, the through hole 42a, both end portions of the axial _{JB 11} direction of the cross bearing 14 are inserted respectively into 44a, socket yoke 11 about the axis _{JB 11} cross bearing 14 It can be turned.

In addition, the flange portion 43 is formed with a through hole 43a in a direction orthogonal to the axial direction thereof similarly to the flange portion 42, and the flange portion 45 has a through hole 45a on the side facing the through hole 43a. Both ends of the cross bearing 15 in the direction of the axis JB ₁₂ are inserted into the through holes 43a and 45a, respectively, and the pin yoke 12 is centered on the axis JB ₁₂ of the cross bearing 15. It can be turned.

  The cross bearing 14 includes a cross shaft having two shafts orthogonal to each other, and bearing cups mounted on both ends of each shaft and having a bearing such as a needle bearing, for example. Are mounted in the through holes of the socket yoke 11 and the through holes of the coupling yoke 13. Similarly to the cross bearing 14, the cross bearing 15 includes a cross shaft having two axes orthogonal to each other, and a bearing cup that is attached to both ends of each shaft and has a bearing such as a needle bearing. Each bearing cup is mounted in each through hole of the pin yoke 12 and each through hole of the coupling yoke 13.

Next, the operation of the double cardan joint 10 will be described.
7 is a cross-sectional view showing the AA cross section in FIG. 3 of the double cardan joint 10 according to the embodiment of the present invention. FIG. 7A shows a relative angle α between the socket yoke 11 and the pin yoke 12. shows the swing state _1, FIG. 7 (b) shows a state where the socket yokes 11 and Pin'yoku 12 is swung at a relatively angles beta _1.

As shown in FIG. 7 (a), a socket yokes 11 and Pin'yoku 12 swings relative direction of the arrow, the socket yoke 11 about the axis JB ₁₁ attempts rotated in the arrow direction, Pin'yoku 12 also attempts to rotate in the arrow direction about the axis JB _12.
Here, the spherical bearing 16 in the socket yoke 11 is guided by the first spherical bearing guide 47 and the second spherical bearing guide 48 shown in FIG. 5 and slides in the direction of the arrow, and the socket shown in FIG. Guided by the first guide 33 a and the second guide 33 b of the cylindrical portion 33 of the yoke 11, it slides in the distal direction of the cylindrical portion 33. At the same time, the cylindrical portion 37 of the pin yoke 12 slides in the needle bearing 17 in the spherical bearing 16 in the direction of being extracted from the spherical bearing 16.

Thus with spherical bearing 16 slides within the tubular portion 33, since the cylindrical portion 37 slides within the needle bearing 17, the socket yoke 11 is rotated in the arrow direction about the axis JB ₁₁ The pin yoke 12 can also rotate in the direction of the arrow about the axis JB ₁₂ . At this time, the spherical bearing 16 is guided by the first spherical bearing guide 47 and the second spherical bearing guide 48 and can slide in the arrow direction. Spherical bearing 16, since it is regulated so as to slide the first spherical bearing guide 47 along a second spherical bearing guide 48, and the straight line connecting the center Pb and the axis JB ₁₁ of the spherical bearing 16, the axis JB ₁₁ and the straight line connecting the axis JB ₁₂ is α ₁ , and the straight line connecting the center Pb of the spherical bearing 16 and the axis JB ₁₂ and the straight line connecting the axis JB ₁₁ and the axis JB ₁₂ is α. ₁ and the angle between the two becomes equal.

As shown in FIG. 7B, the spherical bearing 16 slides along the first spherical bearing guide 47 and the second spherical bearing guide 48 even when the swing of the socket yoke 11 and the pin yoke 12 increases. The angle formed by the straight line connecting the center Pb of the spherical bearing 16 and the axis JB ₁₁ and the straight line connecting the axis JB ₁₁ and the axis JB ₁₂ is β ₁ , and the center Pb of the spherical bearing 16 and the axis JB ₁₂ are connected. The angle formed by the straight line and the straight line connecting the axis JB ₁₁ and the axis JB ₁₂ is β ₁ , and the angles formed by both are equal.

FIG. 8 is a cross-sectional view of the double cardan joint 10 according to the embodiment of the present invention taken along the line CC in FIG. 2, and FIG. 8 (a) shows that the socket yoke 11 and the pin yoke 12 are relatively at an angle α. shows the swing state in _2, FIG. 8 (b) shows a state where the socket yokes 11 and Pin'yoku 12 is swung at a relatively angle beta _2.

As shown in FIG. 8 (a), a socket yokes 11 and Pin'yoku 12 swings relative direction of the arrow, the socket yoke 11 about the axis EN ₁₁ attempts rotated in the arrow direction, Pin'yoku 12 also attempts to rotate in the arrow direction about the axis EN _12.
Here, the spherical bearing 16 in the socket yoke 11 is guided by the first spherical bearing guide 47 and the second spherical bearing guide 48 and moves in the direction of the arrow, and the cylindrical shape of the socket yoke 11 shown in FIG. Guided by the first guide 33 a and the second guide 33 b of the portion 33, it slides in the distal direction of the tubular portion 33. At the same time, the cylindrical portion 37 of the pin yoke 12 slides in the needle bearing 17 in the spherical bearing 16 in the direction of being extracted from the spherical bearing 16.

Thus with spherical bearing 16 slides within the tubular portion 33, since the cylindrical portion 37 slides within the needle bearing 17, the socket yoke 11 is rotated in the arrow direction about the axis EN ₁₁ The pin yoke 12 can also rotate in the direction of the arrow about the axis JA ₁₂ . At this time, the spherical bearing 16 is guided by the first spherical bearing guide 47 and the second spherical bearing guide 48 and can slide in the arrow direction. Since the spherical bearing 16 is restricted to move along the first spherical bearing guide 47 and the second spherical bearing guide 48, a straight line connecting the center Pb of the spherical bearing 16 and the axis JA ₁₁ and the axis JA _11. the axis _{EN 12} and _two straight lines and the angle is α connecting a straight line connecting the center Pb and the axis _{EN 12} of the spherical bearing 16, the axis _{EN 11} and the axis _{EN 12} and ₂ angle between straight line α connecting And the angle between them is equal.

As shown in FIG. 8B, the spherical bearing 16 moves along the first spherical bearing guide 47 and the second spherical bearing guide 48 even when the swing of the socket yoke 11 and the pin yoke 12 increases. The angle formed by the straight line connecting the center Pb of the spherical bearing 16 and the axis JA ₁₁ and the straight line connecting the axis JA ₁₁ and the axis JA ₁₂ is β ₂ , and the straight line connecting the center Pb of the spherical bearing 16 and the axis JA ₁₂ And the angle formed by the straight line connecting the axis JA ₁₁ and the axis JA ₁₂ is β ₂ , and the angles formed by both are equal.

  When the spherical bearing 16 moves in the direction of the arrow shown in FIGS. 8A and 8B, the first spherical bearing guide 47 and the second spherical bearing guide 48 also move in the direction of the arrow together with the spherical bearing 16. The first leaf springs 51 and 52 provided in the first spherical bearing guide 47 and the first leaf springs 61 and 62 shown in FIG. 4 contract. On the other hand, since the second leaf springs 53 and 54 provided on the second spherical bearing guide 48 and two second leaf springs (not shown) are extended, the spherical bearing 16 is always in the first position regardless of the magnitude of movement. The first spherical bearing guide 47 is in contact with the circular arc surface 47 a of the spherical bearing guide 47 and the second spherical bearing guide 48 is in contact with the circular arc surface 48 a. When the spherical bearing 16 returns in the direction opposite to the arrow, the first plate springs 51 and 52, the second plate springs 53 and 54, the first plate springs 61 and 62 shown in FIG. 4, and two second springs (not shown). Therefore, the spherical bearing 16 contacts the arc surface 47a of the first spherical bearing guide 47 and also contacts the arc surface 48a of the second spherical bearing guide 48.

  Thus, in the double cardan joint 10 according to the present embodiment, the socket yoke 11 and the coupling yoke 13 coupled to the socket yoke 11 via the cross bearing 14 having two axes orthogonal to each other are orthogonal to each other. A pin yoke 12 connected to the coupling yoke 13 via a cross bearing 15 having two shafts, and a spherical bearing 16 which is accommodated in the socket yoke 11 and flexibly couples the socket yoke 11 and the pin yoke 12. The socket yoke 11 has a cylindrical portion 33 that slides the spherical bearing 16 in the axial direction of the socket yoke 11, and the coupling yoke 13 extends in a direction perpendicular to the axial direction of the coupling yoke 13. The first spherical bearing guide 47 and the second spherical bearing guide 48 are slid. And, Pin'yoku 12 are characterized by having a cylindrical portion 37 which slides in a through hole 16a formed in the spherical bearing 16.

  In this case, the spherical bearing 16 slides in the axial direction of the socket yoke 11 in the cylindrical portion 33 of the socket yoke 11, and the cylindrical portion 37 of the pin yoke 12 is within the through hole 16 a formed in the spherical bearing 16. Therefore, the spherical bearing 16 can be reliably slid in the direction perpendicular to the axial direction of the coupling yoke 13 by the first spherical bearing guide 47 and the second spherical bearing guide 48 of the coupling yoke 13. it can. As a result, the movement of the spherical bearing 16 is regulated in the sliding direction by the first spherical bearing guide 47 and the second spherical bearing guide 48, so that the socket yoke 11 and the pin yoke 12 are bent via the spherical bearing 16. The angle formed by the straight line connecting the center of the spherical bearing 16 and the rotation center of the socket yoke 11 and the straight line connecting the rotation center of the socket yoke 11 and the rotation center of the pin yoke 12 is the center of the spherical bearing 16. The angle formed by the straight line connecting the rotation center of the pin yoke 12 and the straight line connecting the rotation center of the socket yoke 11 and the rotation center of the pin yoke 12 is equal. Therefore, the socket yoke 11 and the pin yoke 12 rotate at a constant speed. For example, the joint angle between the first propeller shaft 3 connected to the socket yoke 11 and the second propeller shaft 4 connected to the pin yoke 12. Even if changes, excellent constant velocity can be obtained at all times, and a reduction in torque transmission efficiency can be prevented.

  Further, in the double cardan joint 10 according to the present embodiment, the coupling yoke 13 has the first leaf springs 51, 52, 61, 62 for pressing the spherical bearing 16 by the first spherical bearing guide 47, and the first Since the second spherical springs 53 and 54 for pressing the spherical bearing 16 by the two spherical bearing guides 48 and the other two second leaf springs are provided, the spherical bearing 16 is reliably slid. The spherical bearing 16 can suppress vibrations generated in the first spherical bearing guide 47 and the second spherical bearing guide 48, and noise is reduced. Further, when the spherical bearing 16 attempts to return to the original position, each leaf spring can reliably return the spherical bearing 16 to the original position.

  In the double cardan joint 10 according to the present embodiment, the coupling yoke 13 is arranged in a direction orthogonal to the direction in which the spherical bearing 16 slides by the first spherical bearing guide 47 and the second spherical bearing guide 48. The first spherical bearing guide 47 is slid in the through hole 41a, and the through hole 41b is formed so as to face the through hole 41a with the spherical bearing 16 interposed therebetween. The second spherical bearing guide 48 is configured to slide in the hole 41b.

  In this case, the spherical bearing 16 can be moved in a direction orthogonal to the sliding direction by the first spherical bearing guide 47 and the second spherical bearing guide 48, and the socket yoke 11 and the pin yoke 12 are moved to the first spherical surface. Even when the bearing guide 47 and the second spherical bearing guide 48 are swung in the direction orthogonal to the sliding direction, the straight line connecting the center of the spherical bearing 16 and the rotation center of the socket yoke 11 and the socket yoke 11 Between the rotation center of the pin yoke 12 and the angle formed by the straight line connecting the rotation center of the pin yoke 12 and the straight line connecting the center of the spherical bearing 16 and the rotation center of the pin yoke 12. The angle formed by the straight line connecting the rotation center is equal. As a result, the socket yoke 11 and the pin yoke 12 rotate at a constant speed. For example, a joint between the first propeller shaft 3 connected to the socket yoke 11 and the second propeller shaft 4 connected to the pin yoke 12 is used. Even if the angle changes, excellent constant velocity is always obtained.

FIG. 9 is a schematic diagram of the double cardan joint 10 according to the embodiment of the present invention. FIG. 9A shows a state in which the angle formed by the socket yoke 11 and the pin yoke 12 is α ₃ , and FIG. ) is the angle socket yokes 11 and Pin'yoku 12 indicates the state of the beta _3.
10, as described above, the joint angle formed by the straight line connecting the axis _{JB 12} axis _{JB 11} and Pin'yoku 12 socket yoke 11 and one of the axis and the socket yoke 11 of Pin'yoku 12 (deg), the socket 6 is a graph showing a relationship with an angular velocity (rad / s) of either a yoke 11 or a pin yoke 12.

As shown in FIG. 9, the double cardan joint 10 according to this embodiment, when the joint angle formed by the socket yoke 11 and Pin'yoku 12 became alpha _3, the axes of JB ₁₁ and Pin'yoku 12 of the socket yoke 11 An angle θ ₁ formed by a straight line L connecting JB ₁₂ and a straight line ΔL ₁ connecting the axis JB ₁₁ and the center Pb of the spherical bearing 16, and a straight line connecting the straight line L, the axis JB ₁₂ and the center Pb of the spherical bearing 16. The angle θ ₂ formed by ΔL ₂ becomes equal. That is, since the distance ΔL ₁ is equal to the distance ΔL ₂ , the angular velocity ω ₁ (rad / s) of the socket yoke 11 is equal to the angular velocity ω ₂ (rad / s) of the pin yoke 12. The pin yoke 12 rotates at a constant speed.

This rocking of the socket yokes 11 and Pin'yoku 12 increases, as shown in FIG. 9 (b), even when the joint angle formed by the socket yoke 11 and Pin'yoku 12 becomes beta _3, the joint angles it is similar to that of the alpha _3. That is, the straight line L connecting the axis _{JB 12} axis _{JB 11} and Pin'yoku 12 of the socket yoke 11, the axis _{JB 11} and the straight line DerutaL' ₁ and the angle [theta] & apos ₁ connecting the center Pb of the spherical bearing 16, linear An angle θ ′ ₂ formed by a straight line ΔL ′ ₂ connecting L, the axis JB _12, and the center Pb of the spherical bearing 16 becomes equal. That is, since the distance between the distance DerutaL' ₁ of DerutaL' ₂ are equal, the angular velocity ω ₂ (rad / s) of the angular velocity ω ₁ (rad / s) and Pin'yoku 12 sockets yoke 11 and are equal, the socket York 11 and the pin yoke 12 rotate at a constant speed.

  As shown in FIG. 10, in the double cardan joint 10 according to the present embodiment, the angular velocity (rad / s) is constant regardless of the joint angle, and there is no change in the angular velocity. 11 and the pin yoke 12 always rotate at the same speed. In other words, the first propeller shaft 3 as the input shaft connected to the socket yoke 11 and the second propeller shaft 4 as the output shaft connected to the pin yoke 12 are not affected by changes in the joint angle. Has speed.

  In the double cardan joint 10 according to the present embodiment, the first plate springs 51 and 52 are provided on the side surface 47b of the first spherical bearing guide 47, and the first plate springs 61 and 62 are provided on the side surface 47c. The second spherical bearing guide 48 is also provided with the second leaf springs 53 and 54 on the side surface 48b and the other two second leaf springs on the side surface 48c. However, in the double cardan joint according to the present invention, May be provided with one leaf spring on each side surface of the first spherical bearing guide and the second spherical bearing guide, or only on one side surface of the first spherical bearing guide and the second spherical bearing guide. May be provided.

  Further, the first spherical bearing guide and the second spherical bearing guide may be provided with other pressing means for pressing the spherical bearing. For example, the first or second pressing means may be constituted by an elastic body such as a compression coil spring, and the first spherical bearing guide and the second spherical bearing guide may press the spherical bearing. The first spherical bearing guide and the second spherical bearing guide may press the spherical bearing. Further, the first spherical bearing guide and the second spherical bearing guide itself are made of an elastic body such as rubber or plastic so that the first spherical bearing guide and the second spherical bearing guide press the spherical bearing. Also good.

  As described above, according to the present invention, there is an effect that it is possible to provide a double cardan joint having excellent constant velocity that is not affected by a change in the joint angle between the input shaft and the output shaft. It is useful for universal joints such as joints and constant velocity universal joints.

It is a top view of the propeller shaft to which the double cardan joint which concerns on the 1st Embodiment of this invention is applied. 1 is a plan view of a double cardan joint according to a first embodiment of the present invention. It is a side view of a double cardan joint concerning a 1st embodiment of the present invention. It is sectional drawing which shows the AA cross section of FIG. It is sectional drawing which shows the BB cross section of FIG. It is sectional drawing which shows CC cross section of FIG. It is a sectional view showing the A-A cross section in FIG. 3 of the double Cardan joint according to an embodiment of the present invention, FIG. 7 (a), a state in which the socket yoke and Pin'yoku swings at a relatively angles alpha ₁ shown, FIG. 7 (b) shows a state in which the socket yoke and Pin'yoku swings at a relatively angles beta _1. Is a sectional view showing a section C-C in FIG. 2 of a double Cardan joint according to an embodiment of the present invention, FIG. 8 (a), a state in which the socket yoke and Pin'yoku swings at a relatively angle alpha ₂ shown, FIG. 8 (b) shows a state in which the socket yoke and Pin'yoku swings at a relatively angle beta _2. Is a schematic view of a double cardan joint according to the embodiment of the present invention, FIG. 9 (a), a socket yoke and Pin'yoku indicates the state of the angle is alpha _3, FIG. 9 (b), the socket yoke and Pin'yoku Shows the state where the angle formed by is β ₃ . The joint angle formed by the axis of one of the socket yoke and the pin yoke of the double cardan joint according to the embodiment of the present invention and the straight line connecting the axis of the socket yoke and the axis of the pin yoke, and the angular velocity of either of the socket yoke or the pin yoke It is a graph showing the relationship. 11A and 11B are schematic diagrams of a conventional double cardan joint, in which FIG. 11A shows a state where the angle formed by the input shaft and the output shaft is α, and FIG. 9B shows that the angle formed by the input shaft and the output shaft is β The state of ₃ is shown.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Propeller shaft 2 1st joint 3 1st propeller shaft 4 2nd propeller shaft 5 3rd joint 6 Center bearing 10 Double cardan joint 11 Socket yoke (1st yoke)
12 pin yoke (third yoke)
13 Coupling yoke (second yoke)
14 Cross bearing (first cross shaft)
15 Cross bearing (second cross shaft)
16 Spherical bearing 16a, 32a, 32b, 36a, 36b, 41a, 41b, 42a, 43a, 44a, 45a Through hole 17 Needle bearing 18 Retainer 31, 42, 43, 44, 45 Flange part 32, 36, 41 Body part 33 Cylindrical portion 33a First guide 33b Second guide 33c, 33d Groove 36c Other end portion 37 Column portion 47 First spherical bearing guide (bearing guide member)
47a, 48a Arc surface 47b, 47c, 48b, 48c Side surface 48 Second spherical bearing guide (bearing guide member)
51, 52, 61, 62 First leaf spring (first pressing means)
53, 54 Second leaf spring (second pressing means)

Claims (5)

Via a first yoke, a second yoke connected to the first yoke via a first cross shaft having two axes orthogonal to each other, and a second cross shaft having two axes orthogonal to each other And a third yoke coupled to the second yoke, and a spherical bearing housed in the first yoke and flexibly coupling the first yoke and the third yoke. In cardan joints,
The first yoke has a cylindrical portion that slides the spherical bearing in the axial direction of the first yoke;
The second yoke has a bearing guide member that slides the spherical bearing in a direction perpendicular to the axial direction of the second yoke;
The double cardan joint, wherein the third yoke has a cylindrical portion that slides in a through hole formed in the spherical bearing.   The bearing guide member of the second yoke is disposed so as to face the first spherical bearing guide with the spherical bearing interposed between the first spherical bearing guide and the first spherical bearing guide. The double cardan joint according to claim 1, further comprising a second spherical bearing guide for guiding.   The second yoke has first pressing means for pressing the spherical bearing by the first spherical bearing guide, and second pressing means for pressing the spherical bearing by the second spherical bearing guide. The double cardan joint according to claim 1 or 2, wherein the double cardan joint is provided.   The second yoke has a first through hole formed in a direction orthogonal to a direction in which the spherical bearing slides by the bearing guide member, and the first spherical surface is formed in the first through hole. The second spherical bearing has a second through hole formed so as to slide the bearing guide and to face the first through hole with the spherical bearing interposed therebetween, and the second spherical bearing in the second through hole. The double cardan joint according to any one of claims 1 to 3, wherein the guide is slid.   The first pressing means is constituted by a first leaf spring having a bent portion, and one end portion of the first leaf spring is fixed to a side surface of the first spherical bearing guide, and the second pressing means. 5 is constituted by a second leaf spring having a bent portion, and one end of the second leaf spring is fixed to a side surface of the second spherical bearing guide. A double cardan joint according to any one of the claims.

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