JP2015172433A - Roller clutch with seal - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a roller clutch with a seal, wherein rollers inclined with respect to an axis between the inner and outer raceways of a conical single-leaf hyperboloid of revolution are arranged and turned in one direction so that the rollers become engaging elements to confine oil under a contact point with a high pressure thereby to transit an oil film to a viscous fluid, a plastic body and an elastic body with a surface pressure proportional to torque, so that another lubricant is dangerously contaminated to an erroneous action to confine a functional liquid exclusively for a clutch so as to isolate the surrounding lubricant.SOLUTION: A holding member 4 for holding the roller engaging element 3 of a clutch is equipped at its ends with an inner seal lip 17 and a larger diameter side seal lip 21, which contact an inner ring 1 and an outer ring 2 slidably, thereby to establish an oil pack system, in which the clutch is filled with dedicated oil. The space capacity in the clutch is so wide that it can contain a lubricant of a necessary and sufficient quantity.

Description

  Torque transmission device for machinery

  For driving force transmission control of mechanical devices, there are viscous joints, fluid joints, friction plate clutches, gear and claw ratchets, coil spring wrapping friction clutches, 1932 sprag type one-way clutches, and cylindrical rollers and polygons Cam ring one-way clutch, and forward / reverse two-way clutch using it.

  In contrast to these classical techniques, there is a clutch patent 4614167 with an oil film confined under rolling contact. This is because when a roller engaging element inclined between the inner and outer raceway surfaces of a conical single-leaf rotating hyperboloid is interposed, it is meshed when it is turned to one side, and the lubricating oil is confined under an ultra high pressure of 2 to 3 GPa under the contact point of the roller. A solid oil film with a thickness of 0.0003 (0.3 μm) can be formed. In the case of high-viscosity mineral oil, the trapped oil is squeezed out from the periphery of the contact for a long time (one week) to form a squeeze fluid film around the contact. When the roller floats and rolls slightly, oil is newly taken into the contact and a squeeze film is formed. By repeating this, viscous creep (slip) rotates at a constant speed regardless of the magnitude of the torque. This creep rate varies greatly depending on the lubricant and additives and does not creep with ester-based lubricants. When it is turned in the opposite direction, it rotates lightly like an unloaded roller bearing.

  The above-mentioned confined oil film is the elastohydrodynamic lubrication theory (EHL) under rolling contact. Dowson,. Higginson. V. Whitaker: J. et al. Mech. Eng,. 4, 2 (1962) 121. As a result, it was proved that the lubricating oil was confined at a high pressure and transitioned from a viscous fluid to a plastic body and an elastic body, and since then it has made great progress in practical aspects such as rolling bearings and continuously variable transmissions CVT. Recently, the existence of a confined oil film having a thickness of 0.3 μm under the rolling contact at a slow speed has been verified.

Patent registration number 4614167 (Claim 3, FIG. 14) JP 07-071487 JP2011-127563A (FIG. 1) Patent registration number 5352769 (FIG. 14)

The characteristics of the prior art 4614167 are as follows. (1) When a high affinity 6A group transition metal-based extreme pressure additive such as molybdenum disulfide as a layered solid lubricant is added, the affinity between hexavalent chromium on the metal surface and the interlayer Due to the interrelation between the intervening oil molecules, the friction coefficient μ is 0.01 or less under high surface pressure, and the creep rotates at a constant speed regardless of the magnitude of the torque.

(2) The load torque depends on the shear strength of the solidified oil film, and if the strength is low, judder is caused when connecting suddenly.
(3) One-way clutch that locks accurately with ester oil.
(4) When a torque is applied, the inner and outer rings are elastically displaced in the axial direction in proportion to the torque. When the amount of displacement is measured with a linear potentiometer, it becomes a highly accurate clutch and torque sensor that can directly detect the shaft torque. . In this case, an oil agent that is hard to solidify under pressure is preferable in order to quickly return the displacement to the zero point at the moment when the torque is removed.

The above will be described with reference to FIG. 7, which is a specific example. Gears 6 and splines 7 are arranged around bearings 109, 20, 84, 113, and 9 around the central clutch in FIG. Managed. However, the purpose of the above-mentioned (1) creep slip is only for the clutch, (2) the purpose of the one-way clutch, (3) the damper that absorbs torque fluctuation, (4) the function is secured at low or high temperature, (5) torque sensor Uses oils that are hard to solidify under pressure. (6) Safety devices such as reversal prevention use oils that do not freeze at low temperatures, such as squalene that operates reliably even at extremely low temperatures. For clutches only, it is necessary to use the best oil according to the purpose of use.

In particular, it is often used for prevention of reverse rotation to prevent accidents, that is, an important safety location, and it is extremely dangerous if other lubricants are mixed. Therefore, it is indispensable to isolate only the periphery of the engagement roller of the clutch with a special functional oil. Therefore, when dedicated oil seals are provided on the left and right sides of the clutch, a very large space, complexity and cost are required. The original draft of the clutch of this configuration was the public draft Showa 42-752 (filed on March 3, 1964). After that, companies all over the world strove to put it into practical use, but existing one-way clutches historically assumed metal contact. Due to the lack of awareness of the dangers of oils, the accident caused by malfunctions could not be put into practical use for 50 years.

Further, as a means for isolating the conventional one-way clutch from other lubricating oil, the seal structure of the one-way clutch for engine start shown in FIG. It is too big compared to the clutch body.

Furthermore, as a means for adapting the clutch of claim 1 to both forward and reverse rotation, there is JP-A-07-071487 of Patent Document 4, which is provided for each of the two annular holding members in order to reverse the skew direction of the engagement element. A tongue-shaped leaf spring that is in sliding contact with the track is used to make use of the frictional resistance. However, the contact is quickly mirror-finished to become fluid lubrication, and the frictional resistance is rapidly reduced to lose the reversing force. If the spring pressure is increased, the roller is strongly tightened by the holding member with frictional force, and the roller does not roll and slips and does not mesh. In order to prevent this, a planetary roller having different diameters is arranged on the left and right sides of the engagement roller of Patent Document 6 Patent 5352769 (FIG. 14 by the present applicant), and the skew angle is set on the roller by using the principle of causing a delayed advance of revolution on the left and right. It is a mechanism for applying inversion, but it is complicated.

Claim 1 will be described.
The inner ring outer diameter is 8 to 15 degrees with respect to the shaft center on the circumference of the ring between the rotating hyperboloid with the cone angle of 5 to 6 degrees with respect to the axis and the rotating hyperboloid with the same cone angle with the inner diameter of the outer ring. An annular retainer means provided with an inclined slot is provided. The roller of the engagement element is accommodated and held so as to be able to rotate. Then, one side is idled, and in the opposite direction, the oil agent is confined at a high pressure under the contact point, and the oil film transitions to a viscoelastic body at a high pressure, and the roller becomes the clutch system clutch by the shear resistance (traction).

In view of this, an oil pack system is provided in which an oil seal lip is provided on one or both sides of the retainer so as to project the inner and outer diameters in sliding contact with the inner and outer conical raceway surfaces, and dedicated oil is incorporated in the clutch. The mating raceway surface with which the seal lip comes into sliding contact has already been finished with high precision and smoothness as the roller transfer surface.In addition, the error in the raceway spacing between the inner and outer diameters of the seal lip is the biasing force in the thrust direction of the disc spring. Therefore, since the roller is always pressed against the side where the roller is sandwiched and the tolerance of the roller outer diameter is regulated to 0.005 mm, the variation in the tightening margin of the seal lip is automatically within 0.005 mm.
Therefore, when the initial squeeze of the oil seal is set to 0.010 mm, the squeeze of the lip enters a range of 0.015 to 0.025, and the tension force is extremely small and uniform, and the frictional resistance when sliding can be made very small. Naturally, there is little heat generation and wear, and the sealing function is ensured for a long time.

In the seal pack type, the space in the clutch has a large distance between the rollers, so that a necessary and sufficient amount of lubricant can be incorporated. Further, the amount of oil consumed is 0.003 mm when the clutch is locked, the number of rollers on the circumference is about 10, and the amount of rolling with high surface pressure is 60 ° or less in angle and there is no heat generation. In the case of idling to the opposite side, there is almost no deterioration in the consumption of the lubricating oil because it floats to fluid lubrication almost completely with no load only by a light bias of the disc spring.

Therefore, the pack system can cope with any environment and does not require a special seal space, thereby contributing to the function and cost. Also, it is advisable to provide an oil supply hole and a blind plug (FIGS. 6, 52 and 53) on the side of the seal.

The operation mechanism of the forward and reverse clutches according to claim 2 will be described.
Both ends of the roller are engaged with a friction member that is in sliding contact with the inner ring and outer ring that rotate relative to each other, and the roller is tilted to an angle at which the roller can be engaged by frictional resistance with the generated race ring. The frictional force of the friction member is cut off so as not to hinder.

  In the second aspect of the means for obtaining this, the pocket hole for accommodating and holding the roller in the holding member 31 of the roller clutch of the first aspect is formed into a fan-like substantially triangular shape as indicated by 34 in FIG. At one end on the large diameter side of the holding member 31, a V-shaped groove 35 that covers an annular skewer applying member 30 that swings relative to the holding member 31 and engages with the roller end portion is provided. The seal member (17, 21) according to claim 1 is attached to the small diameter side end of the holding member 31. The skew applying member 30 is provided with a plurality of stopper members 33 for regulating the swing range on the circumference, and after the predetermined angle is skewed, the frictional resistance of the seal is cut off so as not to prevent the roller from rotating. The stopper 33 also serves as a hook function that prevents the skew-applying member from coming out of the holding member 31. Thus, skew is applied to the rollers by the arrows 41a and 41b of the long-term stable sliding frictional resistance of the seals (36a and 36b) generated by the relative rotation of the raceway rings, and a roller clutch corresponding to both forward and reverse rotations is obtained.

Here, the driving force for applying the skew to the roller is obtained by the reverse frictional resistance of the inner lip 36a on the large-diameter side and the outer lip 36b on the small-diameter side, so the tension force of the other seal lips 48 and 49 is Minimize. Thus, when the inner and outer rings rotate relatively, they are skewed to the lock side along the direction of relative rotation.

The present invention has the following inventive steps and effects over the background art.
The roller clutch of the present invention is a new oil film clutch that replaces the fluid coupling and plate clutch of the existing clutch, but has the torque characteristics and reliability been obtained because it is inevitably shared with the surrounding lubricating oil? According to the present invention, it is possible to freely select an oil according to the purpose. For example, replacing the conventional disc-type intermittent clutch (commonly called dual clutch) of an automatic gear-type automatic transmission of an automobile with the clutch significantly reduces the torque transfer speed, reduces the shock with a soft elastic engagement, and multi-stages the speed change. The half-clutch range required for torque transfer between gears with different number of teeth is becoming more frequent and is not obtained by slipping the conventional friction disk, but by oil film creep, so it does not wear. The clutch is elastically displaced accurately in the axial direction in accordance with the load torque. Since the ON-OFF control can be performed with a measurement signal of the displacement amount, a further energy saving effect is brought about.

FIG. 1 is a schematic view showing an embodiment of claim 1.
FIG. 2 is an external view of a clutch that is opposed to both directions using the frictional resistance of the seal according to claim 1. FIG. 3 is a schematic diagram of a mechanism for applying a forward and reverse skew. FIG. FIG. 6 shows an embodiment in which a sealing material is applied to the end of a roller holding member.
FIG. 7 shows an embodiment in which claims 1 and 2 are used in a gear transmission.
FIG. 8 shows an embodiment of a conventional one-way clutch sealing mechanism.

A mode for carrying out the invention will be described.
In the embodiment of FIG. 1 of claim 1, standard parts of the inner ring 1, the outer ring 2, and the roller 3 are both ISO standard standard tapered roller bearing material (SUJ-2) accuracy. The holding member 4 holding the roller is made of iron such as S35C or reinforced resin containing 20-30% glass fiber in 66 nylon. A disc spring 45 having a thrust urging force (← mark 47) that ensures the inner ring and the outer ring raceway with the roller are provided. Further, the outer ring 2 has a slide key 61 having a slightly inclined tooth trace (about 3 °) or a scoop spline tooth on the outer diameter of the outer ring 2, and further has a self-lubricating property with a low friction coefficient on the slide sliding surface. Surface treatment or oil dimple processing is applied to shift the axial relative displacement 3 to 5 mm at the time of torque load to assist the engagement of the rollers. Oil seals 17 and 21 are provided at both ends of the holding member, the sealing material is nitrile rubber or acrylic rubber, and a fluoro resin is used for high temperature applications, and the holding member is fitted with an adhesive in the groove as shown in FIGS. Integrate with. The lip shape of the seal is cut with a sharp blade as shown in FIGS.

Both side surfaces of the holding member are positioned in the axial direction with the metal surface exposed and sandwiched between the disc spring 38 and the thrust receiver 58. At the same time, it is supported and centered in the radial direction by the elasticity of the lip of the oil seal provided on the inner and outer diameters of the holding member. This centering form corresponds to a roller guide holder in a roller bearing. Also, the tight force of the seal with the raceway is such that the oil does not leak initially.

FIG. 2 of the embodiment of claim 2 will be described. Triangular pocket holes 34 are formed in the holding member main body 31 at equal intervals on the circumference. One end of the main body 31 is covered with a skew-applying member 30 so that the outer periphery of the main body 31 can be rotated. Tongues 33 serving as stoppers are provided at three locations on the circumference of the skew-applying member 30. After attaching the holding member 31 to the holding member 31, the ribs 50 of the holding member are folded and folded inside the triangular pocket to hold the skew-applying member. The member 31 is swingably movable and loosely fitted so as not to drop off. Oil seals 36a are attached to the side surfaces of the skew applying member and the holding member, respectively, and a garter spring 37 prevents loosening of the tightening force due to lip wear deterioration. The garter spring may be a mold-in type embedded in rubber, and the garter spring may be eliminated as long as the material can maintain the urging force.

The frictional force of the seal repeatedly acts on the side surface of the stopper 33 every time the clutch is turned on and off, and when the seal lip is fixed to the race ring by freezing or rust when starting after extremely low temperature or a long-term stop, the race ring In consideration of these, the rotational force acts through the skew-applying member as it is, and accordingly appropriate strength (heat treatment hardness) is required. A skew imparting member hardens the surface by carburizing or nitriding by press forming of a steel plate. The tongue portion is provided at about three locations on the circumference, and since the bending is performed after the heat treatment, only the bent portion is coated with a carburizing agent before the carburizing treatment in order to prevent cracking.

Embodiment 1 and FIG. 1 show an embodiment in which a rubber seal and a lip projecting to the inner and outer diameters are attached to the end of the holding member.

Example 2 and FIG. 6 are examples in which an oil supply hole and a stopper are provided at one place on the circumference of the holding member 4. Instead of the seal of FIG. 6, a groove is provided in the inner and outer diameters of the holding member and the cross section is X Can be fitted with a square rubber or resin ring (not shown)

Embodiment 3 and FIG. 2 show an embodiment representative of claim 2. FIG. 3 is a diagram for explaining an operation in which a skew is applied to the roller 3 in the triangular pocket 34 with the frictional resistances indicated by arrows 41a and 41b.

Embodiment 4 and FIG. 5 show an embodiment in which a protrusion 44 is provided on the roller and engaged with the groove or hole 43 of the skew applying member 42 to cause the roller to be skewed in conjunction with the frictional resistance of the seal lip 36a. On the contrary, a hole may be made in the end of the roller to make a pin on the skew-applying member side, or both ends of the roller may be made protrusions and the other side may be made a hole. (Not shown)
Embodiment 5 An embodiment in which the present invention is used for a transmission gear is shown in FIG. FIG. 7 shows an example of the ON / OFF operation of the clutch using the lever principle constituted by the rotating shaft 113 of the eccentric cam, the intermediate member 16 and the outer diameter of the cam. Assuming that the worm gear 11 is a power point, the engagement point 112 of the intermediate member 16 is a fulcrum, and the outer diameter of the outer ring 9 is an action point, when the worm gear 11 is rotated by the motor 13, the eccentric cam 9 rotates and pushes the outer ring 2 back to the smaller diameter. Spreads and idles. If the eccentric cam is returned to the original position, it is locked in both forward and reverse directions, or a half-clutch state due to the oil film viscosity is achieved. In these functions, the torque characteristics can be changed for each gear to be used by putting the compatible oil agent and the clutch into the pack by the means of the roller of claims 1 and 2.
Example 6 In the illustrated example, seal members are provided on both sides of the holding member, but when a clutch is used at the end of the input / output shaft, only one side seal is required, or when two clutches are used side by side, If the inner and outer layers are overlapped in the radial direction, only one side seal is required (not shown)
Embodiment 7 In claim 2, the drive source for skew reversal is obtained by the frictional resistance of the seal lip, but if the sealing function itself is not required, the skew imparting member 30 and the holding member 31 can be rotated together with the inner and outer rings. For example, a friction plate, a viscous resistance of oil, or a magnetic fluid may be used as a driving source with less wear and a stable friction resistance (not shown).
The method of the stopper 33 is only one example, and a method of restricting the operating range by engaging a pin on the opposite side with a long hole on the opposite side or engaging a protruding member in the key groove may be used. May be. (Not shown)

If the unit is packed with a functional fluid dedicated to clutches, the clutch in the transmission, variable speed viscous fluid joint (half clutch state), backstop capable of high-speed overrunning, torque limiter, torsional damper, torque sensor, and even impact An energy-saving self-holding type clutch that does not require wear deterioration that does not require an electromagnetic clutch, hydraulic / pneumatic, or electromagnetic force can be obtained.
In particular, if the one-way clutch for auto-rotation of a rotary wing aircraft is replaced with the present invention, the reliability is remarkably improved. It can also be widely used as a power management element such as a hybrid vehicle power distribution device, an automatic transmission, a 4WD vehicle differential limiting device, a variable speed viscous fluid coupling, an engine start clutch, a door closer, and a slow shutter clutch for a fire shutter.

1. Input shaft (inner ring)
2. Output shaft (outer ring)
3. Roller engaging element 4. Holding member 5. Output gear 7. Spline fitting 9. Cam 11. Worm gear 13. Drive motor 14. Inner ring raceway surface 15. Outer ring raceway surface 17. Inner seal lip 21, 21 a... Large diameter side seal lip 21, 21 b... Small diameter side seal lip 24... Thrust receiver 25 .. seal core metal 30, 42.
33 ·· Stopper 34 · · Pocket hole 35 · · Roller-engaged V groove 36a · · Large-diameter side inner ring sliding lip 36b · · Small-diameter side outer ring sliding lip 37 · · Garter spring (stress force retaining spring)
43, 45 ··· Belleville springs 41a and 41b · · Skew imparting drive force (direction to follow the raceway)
··· Engagement protrusion 47 of engagement roller · · Preload bias direction 48 · · Outer diameter sliding contact seal lip 49 · · Inner diameter sliding contact seal lip 51 · · Groove 52 for engagement · · Oil supply hole 53 ·・ Fuel plug 56 ・ ・ Roll caulking location 59 ・ ・ Lock direction 60 ・ ・ Grease and oil seal space 61 ・ ・ Scue key groove 171 ・ ・ Linear potentiometer (torque sensor)

Claims (2)

  The roller is accommodated in an annular roller holding member having a plurality of pocket holes inclined with respect to the axial center between a single-leaf rotating hyperboloid having an inner ring outer diameter and a single-leaf rotating hyperboloid having an inner diameter of a conical outer ring, and is rotated in one direction. In the roller clutch in which the roller becomes an engaging element on the contrary and a high-pressure confined oil film is formed under the contact point, and the transmission of torque between the inner ring and the outer ring is increased or decreased by the transition action of the oil film to the viscoelastic body. A roller clutch with a seal, wherein the holding member is provided with a seal member that slides on the inner and outer rings. A pocket hole for accommodating the roller engaging element of the holding member of the roller clutch according to claim 1 is formed in a substantially triangular shape, and is engaged with one end of the roller at the bottom side of the triangular hole to rotate relative to the holding member to thereby serve as a skewer. In a roller clutch capable of rotating in both forward and reverse directions, provided with an annular skew-applying member to be applied, the seal member according to claim 1 is installed on each of the holding member and the skew-applying member, and the seal member is moved along the inner and outer rings. A roller clutch with a seal, characterized by having a stopper member that causes the roller to squeeze at a certain angle with respect to the shaft center by a rotating force and stops rotation after squeezing.

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