JP5352769B2 - Roller clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To attain improvement of reliability and a new function of a trapped oil film roller clutch interrupting torque by a pressure viscous fluid of a trapped oil film of a rolling face of a roller. <P>SOLUTION: A position in an axial direction of the rolling roller is optimized. Torque is converted into thrust by a cam to assist engagement. A direction of skew is inverted by a differential motion of a planetary roller to correspond to both forward and reverse directions. It serves also as a universal joint by a spherical roller. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

The present invention relates to a torque transmission device.

Patent No. 2903325 for a device for intermittently or adjusting the driving force of a mechanical device In the fluid frictional transmission force limiting device, a roller inclined in three dimensions with respect to the axial center is arranged between the conical raceway surfaces of the inner ring and outer ring, and the contact surface In particular, the present invention relates to a device for confining and solidifying a lubricating oil at a high pressure, and increasing or decreasing the amount of torque transmitted by its shear resistance.
The basis is the British Dowson & Higginson V. Whitaker: J. et al. Mech. Eng, 4, 2 (1962) 121. According to the paper, etc., the high-pressure contact surface such as rolling contact is confined with high-pressure lubricating oil, and the transition to a strong elastic solidified film and under the rolling contact of the recent continuously variable transmission CVT of the vehicle According to the observation result of the National Institute of Advanced Industrial Science and Technology that an oil film remains for one week after the shutdown.
According to the torque transmission by the confining oil film, it has a function similar to the speed control function of the viscous coupling and the centrifugal governor at a substantially equal speed regardless of the magnitude of the torque from a small torque to a huge torque. The high-strength and high-quality spring characteristics due to the elastic deformation of the curved surfaces of the rollers, and the oil film on the rolling surface transitions from high-viscosity fluid to plastic and elastic body, making it possible to tighten firmly while absorbing impact comprising a pos- sibly function, also the fatigue strength of the recent rolling contact, if used under a surface pressure of 2.5 GPa, a rule of thumb that a lifetime is a permanent, no wear, the simple high strength electromagnetic It is known that a self-holding and extremely powerful intermittent clutch that does not require an urging pressure such as force can be obtained.
Regarding this technology, there are many inventions by the present applicant based on Patent No. 2903325.

Japanese Patent Application No. 277047 by the applicant of the present invention makes the rolling element a conical shape with a small angle, and the skew angle is spontaneously generated in the pocket by the differential at the time of rolling.
In the same way, both ends of the roller in FIG. 1 are engaged with a planetary gear, and the rotation angle of the roller is changed in accordance with the revolution phase to make the viscosity sliding speed variable. Similarly, the roller of FIG. 2 is engaged with both ends of a roller by a friction member, and a delayed advancing force is generated by the friction resistance to make the skew angle variable. Similarly, the roller shown in FIG. 2 of JP-A-7-71485 is accommodated in a case that is subdivided on the circumference, and both ends of the case are phased to change the skew angle of the roller to change the speed.

Similarly, in JP 2003-184910 A, the speed of the needle can be varied by grasping the end of the needle protruding from the track of FIG. 1 and changing the skew angle from the outside. Similarly, the axial relative displacement of the raceway shown in FIG. 5 of JP-A-2003-184910 is countered by the Hertz elastic spring of the ball, and the oil film is thickened to increase the viscosity. In the same manner, there is an electromagnetic coil and electric power unnecessary in place of the electromagnetic clutch shown in FIG. In the same manner, by eliminating the sliding key (spline) in the axial direction that hinders the bite of the roller, which was an issue in the implementation of Patent 2903325, instead of providing an intermediate ring and receiving torque on four sides, There are some that double the relative viscous sliding speed of the confined oil film on the contact surface, and double the shock absorption capacity by the axial elastic displacement of the intermediate ring.

Reference 1

Akihiro Kaneda, Hiroshi Suzuki, Hiroshi Nishikawa, Kenji Matsuda, “Dynamic Interaction between Surface Roughness and Viscoelasticity and Solidification Characteristics of Lubricating Oil under EHL”, Grant-in-Aid for Scientific Research, Fiscal Year 2000 (General Research (B) ) Research result report, (1991)

Reference 2

For FY 2003 (16th) Grant Project EMTAF Research Grant Report No. 16 “Establishment of damage prevention method when t-CVT is stopped”: Contents, observation of remaining oil trapped under rolling contact for one week.

  In the configuration of Japanese Patent No. 2903325, when torque is applied, the inner and outer rings are relatively displaced in the axial direction around the roller. Therefore, sliding contact spline fitting is required on the transmission path. However, there was a fatal problem that the relative displacement was hindered and the clutch did not work due to the friction of the sliding surface, variation, foreign matter, rusting, and catching when moving from static friction to dynamic friction. As a countermeasure, Japanese Patent Application Laid-Open No. 2007-162926 that invented spline sliding contact was invented. Further, when used as an intermittent clutch, in order to cope with forward and reverse rotation, as shown in FIG. 5 described in the application of the above-mentioned Japanese Patent Application Laid-Open No. 2007-162926, a separate roller row for reverse rotation and reverse rotation is required. . Furthermore, in the case of a one-clutch that rotates at a high speed toward the free side, the roller is centrifugally pulled out to the large diameter side along the inner peripheral conical surface of the outer ring in FIG. 3, and at the same time, the skew roller is pressed against the raceway surface by centrifugal force. Since it rolls to the right, it is pushed out as shown by reference numeral 1.

The centrifugal force, the edge of the nail captive roller pocket holes of the retainer in FIG. 2, reference numeral 3, to cause uneven wear slip can not rotate crowded eating a roller. In addition, when a continuous viscous rotation is performed by applying torque, the roller has a friction coefficient difference depending on the roughness of the inner and outer rolling surfaces and the thickness of the oil film. When the inner ring of the small diameter side to the lower bias in the smaller diameter side in the gravity roller and retainer, when there is a flange as 38 in FIG. 5, not from rolling impinge obliquely on the corner portion of the roller edge flange as shown in FIG. 6 Slipping into a viscous torque transmission.

To list the problems in the implementation of Patent 2903325 in this configuration, in order to transmit torque in both the forward and reverse directions, first, depending on the direction of rotation of the raceway, quickly all rollers are simultaneously locked at the same angle. Make it skewered.
Secondly, during the forward and reverse rotation, when for skew direction reversal, once freed away from the track of the roller nip contact restraint on both raceway surfaces, reversing the skew angle causes then again tight-holding, the bearing ring It requires axial displacement operating means.
Third, in the initial stage of starting the suction of the track with the axial component of the traction of the trapped oil film by the roller, the transition from the static friction to the dynamic friction of the starting frictional resistance at the sliding contact point of the race ring that hinders relative displacement A means for assisting the meshing of the rollers is provided by generating a thrust that overcomes factors such as resistance to fluctuations at the time, contamination by foreign matter on the sliding contact surface, rust, and resistance due to step wear. Furthermore, at the initial stage of meshing, the roller is always restricted to the optimum position.
Fourthly, in preparation for abnormal input such as excessive input and impact input, a safety measure for interrupting or mitigating torque is required.
Fifth, it requires a universal joint function that relieves mounting errors between the input and output shafts due to deflection of the mounting portion input shaft , dynamic elastic deformation, misalignment, angular error, and strain that are unavoidable in practice .

The present invention has the following inventive steps and effects over the background art.
In the present invention, a thin oil film of only 0.0003 mm is confined under an ultrahigh pressure of 3,000 to 50,000 atm under rolling contact, and a high viscosity oil freezes and remains for a long period of one week even at rest. Based on the recent observation results such as, with the shear resistance and plastic deformation resistance of the frozen solidified film, the torque in both forward and reverse directions is zero to direct connection, and the shock is elastically and viscously absorbed and synchronized firmly Provided is a self-holding type that does not require auxiliary force such as electromagnetic force with excellent responsiveness, light weight, high torque, wear-free, energy-saving clutch in both forward and reverse directions, and a viscous free joint.

Cross-sectional schematic view of the basic configuration of the present invention Action diagram of roller centrifugal force on cage hole Explanatory drawing of centrifugal force action of roller Revolving differential explanation diagram of planetary roller Illustration of interference between roller end face and ridge Illustration of interference between roller end face and ridge Claims 1, 2 and 3 embodiment cross-sectional schematic view Planetary roller embodiment schematic view Planetary roller embodiment schematic view A schematic view of an embodiment of the torque-converting cam according to claim 2 Example of simultaneous crimping to the raceway in the stacked type Axial elastic displacement curve of laminated inner and outer rollers Example of simultaneous contact of stacked intermediate ring split Example of planetary roller arrangement Example of applying skew by planetary roller, outline drawing Example of stacked forward / reverse bidirectional clutch Viscous free joint with spherical roller, action illustration Viscous free joint of spherical roller, example schematic view Example of giving a planetary roller to a universal joint

The form of claim 1 will be described. To prevent the problem that the position of the roller during idling will be biased by rolling, the polarization Selle force in the thrust formed by skew rolling of the rollers when the rolling emerged in and the oil film with no load Since it is slight, in order to prevent the displacement, a soft elastic stopper (shown by a disc spring 4 in FIG. 7) is applied to the side surface of the cage 6, and the roller inside the cage pocket is rotated. It is enough to push it back to the side away from the collar 38 shown in FIG . In high-speed free rotation, the roller has a thrust component according to the skew angle due to the surface pressure generated by the centrifugal force with the outer ring raceway as shown in FIG. 3, and the force that pulls out along the conical slope by the centrifugal force of the roller itself. A large pulling force of 1 is generated, and thus the cage generates a thrust force that is several times the number of rollers. Therefore, the side surface of the cage must be supported by a smooth surface or the thrust ball bearing 39 of FIG . That is, the cage is sandwiched between an elastic member on the small end side and a thrust bearing on the large end side to strictly regulate the axial position of the cage.

The form of claim 2 will be described in detail.
First, the operation of reversing the presumed skew direction will be described with reference to FIG.
The end of the roller 37 (cylindrical or spherical surface) is loosely fitted to the annular member 6 provided on the small diameter side of the conical track and the upper member 5 provided on the large diameter side of the conical track shown in FIG. Grooves 57a, 57b are provided, and both ends of the rollers 57a, 57b are engaged and rolled. The planetary roller is sandwiched between the inner and outer race rings and turns in the direction of arrow 77a in FIG. 19 as the race ring rotates in accordance with the principle of the turning motion of the conical roller in FIG. In the reverse rotation, it turns in the direction of 77b, and the turning range is restricted to the range of the protrusions 8 and 9 on the tongue provided on the ring upper member 5. As the planetary rollers 57a and 58a turn, the upper ring members 5 and 6 are displaced on the revolution, and both ends of the roller 37 engaged therewith are displaced. As shown in FIG. -Θ is applied to the roller. As described above, the cam means consists of two faces inclined with respect to the shaft center so that it can handle both the skew angle locked forward and the skew angle locked backward. Assist displacement .
For example, as shown in FIG. 7, when fitted with the input shaft and the inner ring inner diameter in the inclined cam 73 of FIG. 9, since the inner ring side has already sliding resistance by the disc spring 56, first the friction when the load torque in resistance torque, helical cam 73, occur, slight thrust 74 by, it adds the suction force and by the contact surface pressure of the original pressing force and be fed roller of the disc springs 56, when there torque is input to the Even if the axial force 74 is converted by the helical cam 73 of FIG. 9 and the mating surface is rusted, the clutch is firmly locked by the assist of the cam. The relative displacement amount of the elastic axial leading to the lock being sucked inner ring to the outer ring so takes more than 5 mm to allow the displacement, provided the slack 76 of Figure 9 the values in terms of the circumferential direction. Further, the sliding surface 73 of the cam is covered with a fluorine resin or the like so that the sliding friction coefficient μ is 0.03 or less.

The form of claim 3 will be described in detail. Japanese Patent Laid-Open No. 6-137344 (the present inventor) has already disclosed a means for reversing the roller skew direction, which is driven by sliding friction with the raceway. However, there is a risk that the frictional member that is in sliding contact with the raceway will be worn away and the friction may be lost after long-term use, and is accompanied by frictional loss during idling. Also, since the skew is quickly reversed, there is no effect of once releasing the roller from the track, that is , increasing the track interval for facilitating the reversal. In contrast, where indicated by the lead line in Figure of the present application 4, when rolling the conical roller, the rollers using the principles pivots differential around the cone vertex 77, the conical roller at both ends of the raceway surface divided into the larger diameter side and the smaller diameter side, and each of an elastic material, for example a planetary rollers 57, 58 shown in FIG. 4 made of a coil spring, to the revolving in orbit and, revolving distance of 4 It looks like the difference between the lengths of 59 and 60 in arcs . When this is sandwiched between the inner and outer races and rotated relative to each other, the smaller diameter side of the roller is delayed with respect to both raceway surfaces, and the larger diameter side rolls ahead. As a result, the coil spring roller itself sandwiched between the two tracks spontaneously generates a skewing force with a differential from the track surface. The annular member 5, 6 of the pocket inner groove of the divided left and right retainer 14 put the planetary rollers 57 and 58 is rolled, a roller 37 for torque transmission to the lead-lag of the left and right Interlock and skew to the side where the wedge action occurs . Since the planetary roller is still in the original skew direction when the raceway begins to reverse, the raceway is displaced to the side that is once separated by the axial component of the traction of the planetary roller. Once released from restraint. Next, as the reversal of the trajectory proceeds, the skew direction reverses and this time the planetary roller generates thrust on the side that narrows the distance between the trajectories to assist the engagement of the torque transmission roller.

FIG. 7 shows a case where the above configuration is implemented based on the above-mentioned Patent No. 2903325 . Regardless of whether the rotation is forward or reverse, the elastic contact pressure of the coil springs 57, 58, the skew angle, and the delay advance due to the differential thereof , the orbital spacing is separated, and as the rotation proceeds, the skew of the 57, 58 The direction is reversed, the direction is changed to suction force, and the track interval is narrowed. At the same time , the torque load roller is skewed and locked. When the rod 20 in FIG. 7 is pushed to the right, the inner ring 35 moves backward to the right, the roller and the track are separated, and the clutch is disengaged. Omitting the biasing of 20, the inner ring is pushed back to the left by the spring 56, the rollers Sucking write Murrell therefore surface pressure in spring effect of elevated Hertz elastic, shock meshing occurs a difference in rotational speed of the inner and outer rings while absorption, then the oil film trapped with a surface pressure increase leads to firmly fastened solidified traction oil film.
When the input torque disappears, the roller is discharged from the track by the elastic restoring force (spring back) of the track and the thawing of the oil film. The planetary roller moves away from the orbit while the rod 20 is operating , does not roll, and rolls only at the moment of forward and reverse rotation. If there is an impact or excessive input, the intermediate ring 35 is elastically displaced in the left direction, collides with the stopper 94, and the roller slips to release the overload.

The connecting shafts of the planetary rollers (elastic rolling elements) 40 and 79 at both ends of the track in the embodiment of FIG. 14 are engaged with the holes of the tongue 46 of the retainer 6, and the tongue 46 is the retainer on the opposite side. The amount of movement is limited between the side surfaces of the projections 8 and 9 extending from 5, and the planetary roller rolls with a delayed advance on the revolution track surface within this range. The skewing force applied to the rollers by the planetary rollers 40 and 79 is stable because it is determined by the product of the elastic contact pressure in the radial direction of the coil spring and the friction coefficient. In addition, the necessary tangential force (traction) is small just by scoring the torque load roller floating from the orbit, and the roller in the torque load state rolls at high surface pressure and stops or moves at a slow speed. Rolling frictional resistance of the roller is not affected.

This structure will be described with reference to FIG. 15 in which a laminated type using an intermediate ring is disclosed in Japanese Patent Laid-Open No. 2007-162926.
A roller 14 is interposed between the shaft 11 and the intermediate ring 12 in FIG. 15, and rolling elements 7 and 10 made of a coil spring of a planetary roller are arranged to revolve at both ends of the track . Similarly, a roller 37 is interposed between the intermediate ring 12 and the outer ring 15, and coil spring rolling elements 17 and 18 of the planetary roller are arranged to revolve at both ends thereof. The mechanism is that when the inner ring 11 is rotated, the intermediate ring is rotated by the frictional resistance of the disc spring 13 , and the outer ring 15 is stationary, so that the outer planetary rollers 17 and 18 roll along with the intermediate ring. Revolves ahead of 17. As a result, skew is applied to the outer roller 37 , and the intermediate ring 12 and the outer ring 15 are engaged and fastened together. Then, the integrated product of the intermediate ring 12 and the outer ring 15 starts to rotate relative to the shaft 11, the inner planetary roller 7 revolves in advance, and the inner roller 14 is given a skew in the locking direction by the differential. This time, the shaft 11 and the intermediate ring 12 are integrated. As a result, the shaft 11 is integrated with the outer ring 15 via the intermediate ring, and torque is transmitted. When reversing, the intermediate ring is pushed back against the disc spring by the axial component force of the traction caused by the planetary roller's own squeeze, the orbital interval is widened, the intervening roller is released and the squeeze reversal is quickly performed. ,make it easier.

When applied to the solenoid coil 19 of FIG. 15, the rod 20 is displaced to the left, the intermediate ring 12 is pushed to the left against the disc spring 13, and is turned off away from the inner and outer raceway surfaces. At this time, when the horizontal axis of the graph of FIG. 11 is the elastic displacement amount δ in the axial direction and the vertical axis is the load torque, the displacement curve of the inner ring roller is 21 and the displacement curve of the outer ring roller is 22. Slip occurs at the point 80 where the difference in displacement occurs, and no more is transmitted. The inner ring contracts with the meshing surface pressure of the roller, the outer ring expands, and the intermediate ring is compressed with high surface pressure from the inner and outer peripheral surfaces and does not deform so much. Therefore, even if the amount of elastic displacement in the axial direction is aligned on the inside, the outside, and even under high torque, there is no automatic slipping. The inner and outer elastic displacements are adjusted by increasing or decreasing the number of rollers.
Also, the curved surface made of a single leaf hyperbola of the inner and outer diameters of the intermediate ring must be in contact with the mating raceway surface through the roller 16 from the no-load stage of the torque. A slit may be inserted as shown in 62, and the intermediate ring is divided into two as shown in 64 in FIG. 10 and connected by a spline, and each of them is crimped to a track by springs 81 and 82 in the axial direction. Alternatively, it can be solved by adjusting in advance with a taper gauge.

The viscous free joint according to claim 4 that relies on the confining oil film will be described in detail.
The invention should, of said patent No. 2903325, within a range not breaking the oil film, while deforming twisting oil film plastic body, intended to transmit torque shear resistance, as shown in FIG. 16, the spherical rollers 27 in the rollers, the rotation Ichiyo hyperboloid orbit of the outer ring, as a concave curved surface of the composite of a circle of curvature, the inner ring outer diameter, are the synthesis concave surface of a large curvature close to a straight line than the outer ring. If the meshing (wedge) angles of all the rollers on the circumference when torque is applied are in the range of 1 ° to 5 °, the clutch is established as a one-way clutch. The principle of the meshing replaced by a planar model shown on the right side of FIG. 16 will be described.
Upper and lower two spherical rollers in marked with bands plates of the gradient of the concave curved surface is skew to the longitudinal direction of the plate, when placed so as to roll in the oblique direction, the plate 25 arrow 28 When displaced in the direction, the rollers 27 and 32 roll on the thick side of the plate in the direction of the arrow 35, that is, on the side where the interval between the plates 23 and 25 becomes narrow, so that the rollers bite between the plates. When the above-mentioned band plate is rounded into a ring, the left figure of FIG . 16 is obtained. This shows a state in which the rotation axis of the outer ring is inclined as shown by 68 with respect to the rotation axis 70 of the inner ring .
Since the roller contact point is close to point contact with the outer convex spherical surface and the concave curved surface of the track, if the crossing angle 68 is 2 ° or less, a wedge effect is produced, and a high-pressure confined oil film is produced, and the transition to the plastic body occurs. A universal joint capable of transmitting viscosity within the torsional deformation range of the oil film is obtained.

Therefore, if the intermediate ring 34, respectively inner roller 51 and outer roller 50 the inner race and the intersection angle of the axis of the outer ring of the right and left 2 ° in Figure 17, until the crossing angle is multiple of 4 ° because double row across catch units allowed It can be established as a universal joint. Since a normal drive transmission shaft (propeller shaft) involves an attachment error, a ball- type constant velocity joint or a hook-type joint is used as a universal joint . However, these universal joints use a needle roller as the rolling element. If the crossing angle is small, the amount of rocking of the rolling element is extremely small, high surface pressure and high-speed rocking with a small amplitude, and grease lubrication . As a result, a fatal pseudo-indentation defect is caused at an early stage. Therefore crossing angle at 2 ° or less that have been impossible use.

An embodiment of claims 1, 2 and 3 is shown in FIG.
In the schematic view of FIG. 7, reference numeral 35 denotes an inner ring of the input shaft, 36 denotes an outer ring of the output shaft, and an angle 8 between the curved surfaces of 35 and 36 which is a single-leaf rotating hyperboloid of a conical surface of about 5 °. A cylindrical roller 37 that is skewed to about 0 ° is interposed in line contact. The roller 37 is accommodated in the pocket grooves of the left and right cages 5 and 6. Although the pressing spring 2 of the roller shown on the lead-out line in FIG. 7 is a coil spring for convenience of explanation, the implementation is a disc spring. With the disc spring 4 of FIG. 7, the roller edge and the edge of the heel are prevented from hitting each other and galling , and the rotation of the roller is not hindered.
The triangular cam 73 in FIG. 7 has a triangular shape with an angle of about 5 ° with respect to the shaft center , and a plurality of triangular cams 73 are provided on the outer periphery of the shaft . When the angle is large, the thrust component in the torque load increases, and the clutch disengagement resistance with the torque loaded increases, that is , the disengagement operation force by 20 increases. Although an example of the cam engaging the inner ring inner diameter 7 may be provided a cam on the outer diameter side of the outer ring.

As shown in FIG. 14, the embodiment of applying the skew according to claim 3 is provided with planetary rollers 46 and 79 made of large and small coil springs on the left and right sides of the roller, and has a tongue-like shape extending in an arm shape from the annular ring 5 to the left. The protrusions 8 and 9 collide with the stoppers 37 and 96 to restrict the amount of skew. The cylindrical rings 41 and 42 in FIG. 8 may be used instead of the coil spring. The divided left and right cages 5 and 6 are provided with guide surfaces 45 and 84 which are in sliding contact with the outer diameter of the roller. The contact elastic deformation amount for obtaining the contact pressure with the orbital surface of the planetary roller is about 1 mm, and if the contact pressure is about 1 kgf, the tangential force (skew imparting force) is 0.15 K kgf per piece. If there are three places on the top, 0.45 kgf of skew imparting force is sufficient. The strength of the applied force is appropriately adjusted by the wire diameter of the coil spring, and the outer circumference is grounded to have an accuracy suitable for rolling. In the embodiment shown in FIG. 15, the rotational hyperboloids of the inner ring and the outer ring are sized with a gauge, and the relative position between the shaft and the outer ring is firmly fixed by the ball bearing 67 with four-point contact. All parts are made of bearing steel SUJ-2, hardened to HRC62-65 by heat treatment, and finished with precision according to JIS of rolling bearings. If the planetary rollers 41 and 42 are disposed on both sides of the cylindrical roller 37 of the torque load roller or the spherical roller (not shown) as shown in FIGS. 8 and 18 in addition to the above-described embodiment, the number of accommodated torque load rollers increases. The torque capacity can be increased. The number of planetary rollers 7 is sufficient if it is three on the circumference as shown in FIG.

FIG. 15 shows an embodiment of a forward / reverse bidirectional clutch when rollers are laminated on the inside and outside, and FIGS. 16 and 17 show an embodiment of a universal joint using a spherical roller according to claim 4.
The ball socket and ball stud 47 shown in FIG. 16 serve as a centering guide when a crossing angle is generated in the inner and outer rings. If a spherical roller is used based on the form of FIG. 5 (not shown) described in Japanese Patent Application Laid-Open No. 2007-162926 , FIG. 17 is obtained. Since the intermediate rings 34 and 85 are integrally fixed and pushed to the right by the disc springs 48 and 49, the spherical rollers 50 and 51 are pressed against the track. Planetary rollers 52 and 53 are arranged at both ends of the spherical rollers 50 and 51, respectively, and opposing skew is applied in both the forward and reverse directions as in FIG. Similarly to FIG. 14, FIG. 19 shows a developed view of the split cage for applying the skew to the roller. In FIG. 17, the outer rings 34 and 86 are held by the centering spacer 71, and 71 is sandwiched between the spherical surface and the spherical surface by the spherical centering spacer 72 pressed by the disc spring 87, and is also centered. . The rollers 50 and 51 are centered and guided by ball bushes 88 and 89 at the center. In other words, the position of the intersection where the input shaft and the output shaft are bent is always an intermediate point between the ball bushings 88 and 89 in cooperation with the spherical spacers 71 and 72 and the ball bushings 88 and 89, so that it is established as a universal joint. Inertia weight 33, when sudden braking from the forward state, is converted into an axial force with a screw 90, the intermediate ring 34 is Desa pushed to the left with respect to the input shaft 95, input shaft this time 95, the output shaft 86 Are connected by two ball bushings 88 and 89, so that only the intermediate ring 34 is removed from the rollers 50 and 51, the torque is instantaneously interrupted, and the differential restriction is released. Parts of fine material the outer diameter accuracy of the planetary roller according to JIS spherical roller bearing is equivalent to the rolling elements of the bearing rolling JIS. The surface of the cage is Katasa HV500 or higher.

  Wide range of applications such as automatic transmissions for vehicle drive systems, differential limiting devices, shock transmission torque transmission devices (torque absorbers), shock-absorbing self-holding full sync clutch devices, viscous fluid joints, and heavy load descent devices Provide energy saving for machine elements.

4 .. Spring 5, 6 .. Divided cage 7, 10, 17, 18, 40, 41, 42, 79, 52, 53, 57, 58 .. Planetary roller 8, 9 Positioning projection 11, 35, 63 -Inner ring (shaft) 12, 34, 85-Intermediate ring 4, 13, 48, 49, 56, 81, 82, 87, 91-Spring 14-Roller 15, 25, 26, 36, 86-Outer ring 16 .. Connecting shaft 19.. Solenoid 20.. Push rod 21.. Axial elastic displacement curve of only inner roller 22.. Axial elastic displacement curve of only outer roller 23, 24.. Inner ring 27, 32, 50, 51..Spherical roller 28, 29, 30, 31..Rotational direction 38 .. 鍔 39, 67..Bearing 46..Stopper 47, 88, 89..Spherical bush 59, 60..Revolution difference 61 .. Track surface 62 ... 64 ·· Spline fitting surface 68 · · Crossing angle 71 · · Centering ring 72 · · Centering auxiliary ring 73 · · Cam 74 · · Thrust 75 · · Torque acting direction · · · Backlash space 33 · · Inertial weight 90 ... Screw 94 ... Stopper

Claims (4)

An inner ring (35) having an outer circumferential surface having a track that forms an inclination with respect to the rotation axis and a curved surface facing the roller, and an inner circumference having a track that forms an inclination with respect to the rotation axis and a curved surface facing the roller A cage (6, 5) for holding a roller having an outer ring (36) having a surface, a side surface (6) located on the small diameter side of the raceway ring, and a side face (5) located on the large diameter side of the raceway ring. And a roller clutch provided with an elastic member (4) that presses the small diameter side of the cage in the axial direction, the roller is tilted so as to be swingable with respect to the rotation axis, and is in line contact and loaded with torque. When this occurs, the torque transmission between the inner ring and the outer ring is increased or decreased by the viscosity of the confined oil film generated by contact between the rollers and the roller, and the smaller diameter side of the cage is reduced by the urging force of the elastic member. The position of the cage is restricted by being pressed The roller clutch, characterized in that. A roller clutch according to claim 1, the torque (75) to assist the engagement of the roller provided with a cam (35) having two surfaces inclined against the axis of the converter (73) to the thrust (74) Characteristic roller clutch. The planetary roller ( 57, 58 ) according to claim 1, wherein an inclination angle of the roller (37) for transmitting torque with respect to a rotation axis of the roller clutch is different in diameter and revolves at both ends of the raceway ring according to claim 1. The roller clutch is provided with a delayed advance occurring at both ends of the roller (37 ) in conjunction with the turning motion (77) . 2. The roller clutch according to claim 1, wherein the raceway curved surface of the outer ring has a radius from the center point of the raceway curved surface of the outer ring and the outer ring raceway to the center of the ball bush provided on the rotation shaft. A roller (37) that is formed of a composite curved surface composed of a spherical surface formed as described above, and that transmits torque, has a center of the curved surface of the outer ring raceway and a center point of the ball bush (47) of claim 1. A roller clutch which is a spherical roller formed of a spherical surface having a length to be joined and a radius of curvature , and which has both a viscous slip and a universal joint function that make a substantially linear contact with both race rings .

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