JPH0771487A - Fluid viscous coupling - Google Patents

Abstract

PURPOSE:To provide a coupling by which a torque characteristic of the coupling can be guaranteed reliably for conversion in the rotational direction and the number of part items can be reduced with a small type and which can be manufactured lightly and by which productivity of a rolling element is improved and reliability becomes high and whose application range is wide in a fluid viscous coupling. CONSTITUTION:A fluid viscous coupling has a cylindrical rolling element 26 housed between an inner ring 6 and an outer ring 18 so as to roll freely, an outside holder 25 to generate rotational resistance between it and the outer ring 18 by spring force by regulating a position of the rolling element 26, an inside holder 24 to generate rotational resistance between it and the inner ring 6 by spring force by regulating a position of the rolling element 26 and a first elastic member 35 to energize the outer ring 18 in the direction for narrowing an interval between orbits of the inner ring 6 and the outer ring 18.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid viscous joint using rolling elements between an inner ring and an outer ring.

[0002]

2. Description of the Related Art As a conventional joint for transmitting torque while allowing a rotation difference,
For example, there is a viscous coupling described in JP-A-2-146320. This joint uses the viscous resistance of fluid and uses silicon oil to stack multiple plates and seal them together with the silicone oil. From the prime mover of a four-wheel drive vehicle to the front wheels. , Or where the drive force is transmitted to the rear wheels, or where the differential rotation of the left and right wheels of the final reduction gear is limited.

However, this joint has the following problems. (1) The number of components is large and heavy. (2) If rotation continues for a long time with a difference in rotation, a hump phenomenon occurs at an unexpected time point, and a large torque is suddenly transmitted. (3) Repeated humps damage the surface of the multi-plate and shorten the life. (4) Since silicone oil has no lubricity, the seal is easily damaged.

In order to eliminate these problems, there has been proposed a fluid friction transmission limiting device as disclosed in, for example, Japanese Unexamined Patent Publication No. 3-204418. This device interposes rolling elements in line contact between the raceways of the shaft and the outer ring, and has means for forming a wedge between the rolling elements by the relative displacement force of the shaft and the outer ring. The amount of force transmission is limited by sliding, and the force is directly connected by a wedge effect for a specific force.

However, this device also transmits torque in the forward rotation direction, but cannot transmit torque in the reverse rotation direction. Therefore, when it is applied as a 4WD joint for automobiles or an LSD joint, the characteristics are always reversed. It is necessary to use two things in combination. For this reason, the structure is large and heavy, and the merchandise is also reduced accordingly. Next, as an improvement of the characteristics of the joint, JP-A-4-219528.
There is one described in the publication.

According to the joint of claim 1 of the same publication, the input torque is arranged between the races of the inner ring and the outer ring so as to be inclined three-dimensionally with respect to the axis of the race, and thereby the input torque is applied to the contact pressure between the rolling elements and the race. The transmission amount of torque is arbitrarily increased or decreased by changing the inclination angle of the shaft of the rolling element. In this joint, both ends of the rolling elements are supported by planetary gears, which is a very complicated and high-grade mechanism, so that it is difficult to apply it to parts for automobiles in terms of cost. In addition, the quality becomes excessive with respect to the required characteristics.

In the joint of claim 2, the distance between the cone centers of the inner ring raceways is made shorter than the distance between the cone centers of the outer ring raceways to automatically oppose the inclination angle of the rolling elements in the direction of relative rotation of the raceways. The cage is provided with means for regulating the inclination angle of the rolling elements. Although the joint of claim 2 has a simple structure, it has the following problems. Although not described in the above publication, the relationship between the inner and outer races and the rolling elements forming this joint can be roughly classified into three cases.

Case 1 is a case where the rolling surfaces of the inner and outer rings are conical and the rolling elements are cylindrical. In case 2, the inner and outer races have conical rolling surfaces, and as shown in FIG. 8, the rolling element uses a deformed cylindrical roller having a cross section near both ends and a concave cross section near the ellipse at the center. That is the case. Case 3 is a case where the rolling surfaces of the inner and outer rings are single-leaf hyperboloids and the rolling elements are cylindrical.

Next, the problems in each case will be described. In case 1, the inner and outer races and the cylindrical rolling element make the most stable contact with each other when the rotation axis of the cylindrical roller is included in the plane including the rotation axes of the inner and outer races. Are two parallel lines of the outer ring and the cylindrical roller, and the inner ring and the cylindrical roller. However, at this time, since no surface pressure is generated between the inner and outer races and the rolling elements, torque is not transmitted.

When the rolling elements are skewed along the fan-shaped cage, the cylindrical roller comes into contact with the outer ring at both ends and the inner ring at the center. When the relative rotation increases in such a hit state, the wedge effect causes the distance between the inner and outer rings to approach, and torque is transmitted. However, since the contact with the cylindrical roller is extremely localized, the surface pressure becomes extremely high.
Normally, the limit of the surface pressure of such a structure is 400 kg / mm ²
Although it is considered to be a degree, since the contact area is small, the torque that can be transmitted is also small. Therefore, although the overall size is large, the coupling torque is small.

Further, bending stress is generated in the cylindrical roller, and when a large torque is applied, the allowable stress is exceeded.
In order to avoid such a phenomenon, it is conceivable that the cylindrical rollers are cut and arranged side by side, but since the cage shape is fan-shaped, the cylindrical roller at the end of the fan spread becomes extremely unstable. It is difficult to shorten the length of such a cylindrical roller to improve the torque capacity.

Next, in case 2, the shape of the cylindrical roller is determined with respect to the design skew angle. The cylindrical roller designed to have a skew angle α with respect to the surface including the rotation shafts of the inner and outer rings provides a stable contact when arranged at two angles of −α. That is, the conical shape at both ends is line contact with the rolling surface of the outer ring, and the central elliptical portion is line contact with the rolling surface of the inner ring. When the relative rotation increases in this state, the wedge effect causes the distance between the inner and outer wheels to approach, and the torque is transmitted.

At this time, the contact with the cylindrical roller is at both ends and at the center collinear contact, as compared with the case 1, so that the surface pressure is improved. However, also in this case 2, since a load is applied to the cylindrical roller from three places, bending stress is generated and only one side is used for the entire length of the cylindrical roller. Although it is large, the joint has a small transmission torque.

Further, considering the time when this joint is switched from the normal rotation to the reverse rotation, both ends are outer rings at the skew angle α at the time of normal rotation.
At the neutral point, the center part was the inner ring and each part was line contact, but at the neutral point, it was sandwiched between the inner and outer rings at the maximum diameter of parts A and B in FIG. The torque in the reverse rotation direction is transmitted. At this time, when the forward rotation side skew angle α and the reverse rotation side skew angle −α are set, the width of the inner ring and the outer ring is minimized, and the width is maximum at the center point where the normal rotation side is switched to the reverse rotation side.

For the cylindrical roller, there is a stable space on the forward rotation side and the reverse rotation side. In this cylindrical roller, all the rollers are simultaneously switched from the forward rotation side to the reverse rotation side or from the reverse rotation side to the forward rotation side. Need to If forward rotation and reverse rotation are repeated in a fan-shaped cage, it cannot be guaranteed that all the cylindrical rollers will always turn in unison. It will remain.

In such a situation, when most of the cylindrical rollers try to transmit torque on the forward rotation side, the cylindrical rollers on the forward rotation side generate a force to bring the inner and outer rings closer to each other, but the cylindrical rollers on the reverse rotation side. Since the roller acts to separate the inner and outer rings from each other, the torque characteristic is greatly deviated from the design specification. In such a state, even though the hole of the cage of the cylindrical roller is fan-shaped, there is a partition wall in the center,
It is difficult for the cylindrical roller to turn over to the normal side.

In the case 3, when the forward rotation side α and the reverse rotation side design angle −α, the inner ring and the cylindrical roller, and the outer ring and the cylindrical roller are in line contact from both sides over the entire length of the cylindrical roller. The surface becomes large and a large torque can be transmitted. Considering when this joint switches from normal rotation to reverse rotation, the forward skew angle α and the reverse skew angle −α
At the center point, the ends of the cylindrical roller, the rolling surface of the outer ring, the central part of the cylindrical roller, and the central part of the inner ring contacted the inner and outer rings in a shape that sandwiched the cylindrical roller from both sides. It will be a local hit.

At this time, the set width of the inner ring and the outer ring becomes the maximum width when the skew angle of the central cylindrical roller is 0, and the set width at the forward rotation skew angle α and the reverse position skew angle −α of the cylindrical roller becomes the minimum. It has the same problem as 2. The present invention has been made in view of such a conventional problem, and can reliably guarantee the torque characteristics of the joint against the conversion of the rotation direction, and uses one rolling element as a whole. It is compact and has a small number of parts, can be made light, has high productivity of rolling elements, has high reliability, and can shorten the dimension in the longitudinal direction. The purpose is to

[0019]

In order to achieve the above object, the present invention provides an outer ring having a conical surface or a single-leaf hyperboloid on its inner diameter and an inner ring having a conical surface or a single-leaf hyperboloid on its outer diameter. A cylindrical rolling element housed between the inner ring and the outer ring so as to be rollable, and an outer cage that regulates the position of the rolling element to generate rotational resistance between the outer ring and the outer ring due to a spring force. An inner cage that regulates the position of the rolling element to generate a rotational resistance between the inner ring and the inner ring by a spring force; and a first biasing the outer ring in a direction that narrows the space between the races of the inner ring and the outer ring. The elastic member is provided.

Further, according to the present invention, when the torque is not transmitted to the opposite side of the first elastic member, it is incorporated in a free state, and when transmitting the torque, the wedge effect by the relative rotation of the inner ring and the outer ring is exerted. A second elastic member for suppressing is provided. Further, according to the present invention, as a means for generating a rotational resistance between the outer ring and the outer ring, a leaf spring portion bent to the outer diameter side is integrally formed on one end side of the outer retainer, and is formed between the outer ring and the inner ring. As a means for generating rotation resistance, a leaf spring portion bent toward the inner diameter side is integrally formed at the other end side of the inner cage.

Further, the present invention is characterized in that fan-shaped housing holes for rotatably holding the rolling elements are formed in the outer cage and the inner cage so as to be symmetrical.

[0022]

According to the fluid viscous joint of the present invention having such a structure, the position of the rolling element is regulated, and the outer cage for generating the rotational resistance between the outer ring and the outer ring is generated, and the position of the rolling element. By using an inner cage that regulates the inner cage to generate rotational resistance with spring force, the outer cage is pressed against the outer ring side by the spring force, and the inner cage is pressed against the inner ring side by the spring force to rotate in the normal direction. The outer cage and the inner cage are forcibly moved so that the rolling elements always turn in the same direction both at the time of reverse rotation and at the same time. it can.

Further, since one rolling element is used as a whole as compared with the conventional example which uses two rolling elements for forward rotation and two rotations for reverse rotation, the joint can be made small, the number of parts is small, and the weight can be reduced. . Further, compared to the conventional example in which various processing is performed on both ends of the rolling element, the rolling element is simple, so productivity is good,
In addition, reliability can be increased.

Furthermore, since the dimension in the longitudinal direction can be designed to be short, the range of application can be expanded to various fields such as a synchro mechanism of a transmission.

[0025]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 7 are views showing an embodiment of the present invention.
FIG. 1 is a sectional view showing an embodiment of the present invention, and FIG. 2 is a side view. First, the configuration will be described. In FIGS. 1 and 2, reference numeral 1 denotes a case such as a transfer device,
One end of an output shaft 3, for example, is rotatably supported by the case 1 via a bearing 2. A male spline 4 is formed on the output shaft 3 and a screw portion 5 is formed on the output shaft 3.

An inner race 6 is fixed to the output shaft 3 as an inner race, and a hollow portion 7 is formed in the inner race 6. A step portion 8 is formed in the hollow portion 7,
A female spline 10 to which the spline 4 of the output shaft 3 is fitted is formed on the small diameter portion 9 on the right side of the step portion 8 in the figure. The inner race 6 and the output shaft 3 are spline-fitted by the splines 4 and 10, and the screw portion 5 and the washer 11 are provided with the step portion 8
Insert it until it abuts and tighten with the nut 12. In this way, the inner race 6 is fixed to the output shaft 3.

The inner race 6 has a single-leaf rotating hyperboloid (wrapping type) 13 on its outer diameter portion as a raceway surface. In FIG. 1, the single-leaf rotating hyperboloid 13 has a cross-sectional shape formed toward the upper right, and grooves 14 and 15 and lands 16 and 17 continuous with the grooves 14 and 15 are formed on both sides thereof. 18
Is an outer race as an outer ring, which has a male spline 19 on its outer diameter portion, and the male spline 19 is fitted to a female spline 22 formed on the inner diameter portion of a housing 21 having a step portion 20. is doing. That is, the outer race 18 is spline-fitted to the housing 21 so as to be slidable in the axial direction.

The housing 21 is connected to an input shaft (not shown) and rotates integrally with the input shaft. In the inner diameter portion of the outer race 18, a single-leaf rotating hyperboloid 23 as a raceway surface is formed facing the single-leaf rotating hyperboloid 13 of the inner race 6. This single-leaf rotating hyperboloid 23 is also formed so that its cross-sectional shape is the upper right corner in FIG. Outer race 18
In the track between the inner race 6 and the inner race 6, a cylindrical roller 26 as a rolling element held by an inner cage 24 as an inner cage and an outer cage 25 as an outer cage is rotatably and rotatably housed.

That is, the cylindrical roller 26 is accommodated in the track so as to be in line contact with the single-leaf rotating hyperboloid 13 of the inner race 6 and the single-leaf rotating hyperboloid 23 of the outer race 18 over their entire lengths. FIG. 3 is a development view of the inner cage 24. As shown in FIG. 3, a fan-shaped storage hole 27 in which the cylindrical roller 26 is rotatably stored is formed in the inner cage 24, and the cylindrical roller 26 is stored in the storage hole 27 with a predetermined skew angle.

A leaf spring portion 28 is formed at one end of the inner cage 24, and the leaf spring portion 28 is bent toward the inner diameter side with respect to the center support portion 29 of the inner cage 24, as shown in FIG. , Land part 1 of inner race 6
It is attached to 7 with pressing force. The center support portion 29 is rotatably attached to the land portion 17 of the inner race 6 by a clearance fit. Further, the end portion 30 on the opposite side of the center support portion 29 is rotatably assembled to the land portion 16 of the inner race 6 by a clearance fit.

FIG. 4 is a development view of the outer cage 25. As shown in FIG. 4, the inner cage 24 has a cylindrical roller 26 rotatably housed in the outer cage 25.
A fan-shaped storage hole 31 that is symmetrical to the storage hole 27 is formed, and the cylindrical roller 26 is stored in the storage hole 31 with a predetermined skew angle. A leaf spring portion 32 is formed at the other end of the outer cage 25, and the leaf spring portion 32 is bent toward the outer diameter side with respect to the center support portion 33 of the outer cage 25. As shown in FIG. It is assembled with a pressing force on the cylindrical surface connected to the single-leaf rotating hyperboloid 23 of 25.

The center support portion 33 is the inner cage 24.
It is rotatably assembled to the outer diameter part of the machine by a clearance fit. Further, the end portion 34 on the opposite side of the center support portion 33 is
It is rotatably assembled to the outer diameter portion of the inner cage 24 by a clearance fit. In this way, the inner cage 24
The leaf spring portion 28 of the outer cage 25 generates a rotational resistance with the inner race 6, and the leaf spring portion 32 of the outer cage 25 generates a rotational resistance with the outer race 18.

A disc spring 35 as a first elastic member is interposed between the housing 21 and the outer race 18, and the disc spring 35 is preloaded so that the cylindrical roller 26 contacts the inner race 6 and the outer race 18, respectively. I'm hanging. That is, the disc spring 35 biases the outer race 18 in a direction in which the cylindrical roller 26 is narrowed by the relative rotation between the inner race 6 and the outer race 18 so that the space between the inner race 6 and the outer race 18 becomes narrower. That is, the disc spring 35 presses the outer race 18 to the right in FIG.

Reference numeral 36 is a disc spring as a second elastic member, and the disc spring 36 is interposed between the side cover 37 assembled to the housing 21 and the outer race 18.
The disc spring 36 is in a free state when torque transmission is not performed, and when the torque transmission is performed, the disc spring 36 is biased in a direction in which the space between the races between the inner race 6 and the outer race 18 is suppressed from becoming narrow. To do. That is, the disc spring 36 pushes the outer race 18 leftward when transmitting torque.

Lubricating oil is enclosed inside the joint,
As the lubricating oil, one having an appropriate viscosity and a high traction coefficient is used. An O-ring 38 is interposed between the housing 21 and the side cover 37, and an oil seal 39 is provided between the side cover 37 and the inner race 6.
Is installed. Also, inner race 6 and case 1
The oil seal 40 is also interposed between them. The O-ring 38 and the oil seals 39 and 40 prevent the lubricating oil from leaking to the outside of the joint. The right movement of the side cover 37 is blocked by the snap ring 41, and the right movement of the side cover 37 is prevented by the land portion 17 of the inner race 6.
Blocked by.

A bolt hole 42 is formed in the housing 21, an input shaft (not shown) is connected thereto, and an opening 43 formed in the housing 21 is closed by a blind plug 44. Reference numeral 45 denotes an X ring interposed between the housing 21 and the inner race 6. Next, the operation will be described.

Referring to FIG. 1 from the left side,
When the housing 21 is rotated to the right and there is a rotation difference between the inner race 6 and the outer race 18,
The outer race 18 rotates in the same direction while dragging the outer cage 25 pressed against the inner diameter of the leaf spring portion 32. On the other hand, since the inner cage 24 is pressed against the land portion 17 of the inner case 6 by the leaf spring portion 28 and has a braking action, the inner cage 24 rotates while being dragged through the cylindrical roller 26. For this reason, the outer cage 25 is dragged and the inner cage 24 is braked. Therefore, the cylindrical roller 26 in the common storage holes 31 and 27 of the outer cage 25 and the inner cage 24 is shown in FIG. It will be aligned as shown.

As described above, when the outer race 18 rotates with the cylindrical rollers 26 aligned, the cylindrical rollers 2
6 enters a track between the inner race 6 and the outer race 18 in a wedge shape, and a strong pressing force is generated in the radial direction. Therefore, the lubricating oil between the inner race 6 and the cylindrical roller 26 and between the outer race 18 and the cylindrical roller 26 receives a large surface pressure.

When a lubricating oil is subjected to a large surface pressure, a viscoelastic body lubricating film is produced, and EHL (Elastro Hydrodynamic Lubrica)
traction coefficient, the traction coefficient between the outer race 18 and the cylindrical roller 26 and between the cylindrical roller 26 and the inner race 6 becomes high, and torque is transmitted. When slow differential rotation continues in this state, the cylindrical roller 26 reduces the sliding wedge effect in this axial direction from the smaller radius of the single-leaf rotating hyperboloids 13, 23 of the inner race 6 and the outer race 18 to the larger radius. .

Therefore, the torque transmitted is performed at a balance between the wedge effect caused by the relative rotation and the axial sliding of the cylindrical roller 26 which reduces the wedge effect. When the relative rotation becomes large, the wedge effect becomes large, and the torque is balanced when the surface pressure becomes high, so that the transmission torque becomes large, and when the relative rotation becomes small, the transmission torque also becomes small.

The relationship between the rotation difference and the torque is as follows: the rigidity of each of the inner race 6 and the outer race 18, the cone angle, the skew angle of the inner cage 24 and the outer cage 25, the diameter of the cylindrical roller 26, and the type of lubricating oil. As a result of various combinations, the disc spring 36 can be used as a means for suppressing and adjusting the wedge effect due to the relative rotation.

When the relative rotation is eliminated, the movement that causes the wedge effect disappears, and the axial load of the cylindrical roller 26 that reduces the wedge effect only occurs due to the distortion due to the torque of each part, so that the radial load on the cylindrical roller 26 is reduced. It does not take. From this state, in reverse, that is, in FIG. 1, when the housing 21 rotates counterclockwise as viewed from the left side of FIG.
Although the outer cage 25 and the inner cage 24 rotate in opposite directions, no unreasonable force is generated in the outer cage 25 and the inner cage 24, and the cylindrical roller 26 changes from the state of FIG. 5 to the state of FIG. Change.

During this period, the state of FIG. 7 is passed, but as is apparent from FIG. 7, the cylindrical roller 26 is supported by the outer cage 25 and the inner cage 24 at both ends, so that it does not cause irregular movement and is cut. Can be exchanged,
It is possible to always obtain a predetermined torque characteristic. Although the case 3 has been described above with respect to the present embodiment, the cylindrical roller 26 can be easily manufactured in this case, but the single-leaf rotating hyperboloids 13 and 23 of the raceways of the inner race 6 and the outer race 18 are not easily formed. There are drawbacks that are difficult to make.

Therefore, when the raceways of the inner race 6 and the outer race 18 are conical as in the case 1 and the case 2, the cylindrical roller 26 can be easily manufactured. This embodiment can deal with both Case 1 and Case 2. In particular, as in case 1, the cylindrical roller 26
Is easy to make, but as described above, the torque capacity is small in one long roller, and the transmission torque capacity can be improved by arranging the rollers in several divisions, but in the present embodiment, Since the cylindrical rollers 26 can be forcibly aligned by the inner cage 24 and the outer cage 25, the case 1 has a large torque capacity and can be easily manufactured.

Further, since one cylindrical roller 26 is used as a whole as compared with the case where two cylindrical rollers for forward rotation and reverse rotation are used as in the conventional case, the size is small and the number of parts is small.
The weight can be reduced. Further, as compared with the conventional example in which both ends of the cylindrical roller 26 are subjected to various kinds of processing, the productivity is good and the reliability can be improved because it is simple.

Further, since the dimension in the longitudinal direction can be designed to be short, the range of application can be expanded to various fields such as a synchro mechanism of a transmission. In addition,
In the present embodiment, the frictional force is applied between the inner cage 24 and the inner race 6 and the outer cage 25 and the outer race 18 by the leaf spring portions 28 and 32, but an elastic member such as an O-ring or the like is provided between them. It goes without saying that sandwiching a friction member or the like can achieve the same purpose.

[0047]

As described above, according to the present invention, by using the outer cage and the inner cage, the outer cage is pressed against the outer ring side by the spring force, and the inner cage is pressed by the spring force on the inner ring side. Since the rolling elements are always pressed in the same direction at the time of forward rotation and reverse rotation, the torque characteristics of the joint can be surely guaranteed against the conversion of the rotation direction.

Moreover, since one rolling element is used as a whole, it is possible to reduce the size, the number of parts, and the weight.
Also, since the rolling elements are simple, they have good productivity,
The reliability can be increased. Furthermore, since the dimension in the longitudinal direction can be designed to be short, the applicable range can be expanded.

[Brief description of drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

[Figure 2] Side view

[Figure 3] Development view of the inner cage

[Fig. 4] Development view of the outer cage

FIG. 5 is a diagram showing the position of a cylindrical roller during normal rotation.

FIG. 6 is a diagram showing a position of a cylindrical roller at the time of reverse rotation.

FIG. 7 is a diagram showing the position of a cylindrical roller when the rotation from normal rotation to reverse rotation has elapsed.

FIG. 8 is a view showing a conventional cylindrical roller.

[Explanation of symbols]

 1: Case 2: Bearing 3: Output shaft 4, 10, 19, 22: Spline 5: Screw part 6: Inner race (inner ring) 7: Hollow part 8: Step part 9: Small diameter part 11: Washer 12: Nut 13, 23: Single-leaf rotating hyperboloids 14, 15: Grooves 16, 17: Land portion 18: Outer race (outer ring) 20: Step portion 21: Housing 24: Inner cage (inner cage) 25: Outer cage (outer cage) 26 : Cylindrical roller (rolling element) 27, 31: Storage hole 28, 32: Leaf spring part 29, 33: Center support part 30, 34: End part 35: Disc spring (first elastic member) 36: Disc spring (first 2 elastic member) 37: side cover 38: O-ring 39, 40: oil seal 41: snap ring 42: bolt hole 43: opening 44: blind plug 45: X-ring

Claims (4)

[Claims] 1. An outer ring having a conical surface or a single-leaf hyperboloid on the inner diameter portion, an inner ring having a conical surface or a single-leaf hyperbolic surface on the outer diameter portion, and rotatably housed between the inner ring and the outer ring. A cylindrical rolling element, an outer retainer that regulates the position of the rolling element to generate rotational resistance between the outer ring and the outer ring, and a spring that regulates the position of the rolling element and the inner ring. A fluid viscous joint comprising: an inner cage that generates rotational resistance by a force; and a first elastic member that urges the outer ring in a direction that narrows a space between raceways of the inner ring and the outer ring. 2. When the torque is not transmitted to the opposite side of the first elastic member, it is incorporated in a free state, and when transmitting the torque, a wedge effect due to relative rotation of the inner ring and the outer ring is suppressed. The fluid viscous joint according to claim 1, wherein the elastic member is provided. 3. As a means for generating a rotation resistance between the outer ring and the outer ring, a plate spring portion bent to the outer diameter side is integrally formed at one end side of the outer cage, and is rotated between the outer ring and the inner ring. 2. The fluid viscous joint according to claim 1, wherein a leaf spring portion bent toward the inner diameter side is integrally formed on the other end side of the inner cage as a means for generating resistance. 4. A fan-shaped accommodating hole for rotatably holding the rolling element is formed in each of the outer cage and the inner cage in a symmetrical manner.
Fluid viscosity joint.