WO1997033105A1 - Poulie a diametre variable - Google Patents
Poulie a diametre variable Download PDFInfo
- Publication number
- WO1997033105A1 WO1997033105A1 PCT/JP1997/000713 JP9700713W WO9733105A1 WO 1997033105 A1 WO1997033105 A1 WO 1997033105A1 JP 9700713 W JP9700713 W JP 9700713W WO 9733105 A1 WO9733105 A1 WO 9733105A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pair
- pulley
- variable diameter
- bodies
- belt
- Prior art date
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/52—Pulleys or friction discs of adjustable construction
- F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
- F16H2061/66295—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the geometrical interrelationship of pulleys and the endless flexible member, e.g. belt alignment or position of the resulting axial pulley force in the plane perpendicular to the pulley axis
Definitions
- the present invention relates to a variable diameter pulley capable of changing an effective radius of a wound belt.
- a belt transmission device has been used to drive, for example, an auxiliary device such as an automobile car compressor or an oil pump.
- the driving force is transmitted from the engine crankshaft via a pulley and a belt at a constant speed ratio, and the rotation speed of each auxiliary machine increases as the rotation speed of the crankshaft increases.
- the efficiency of various accessories also increases with the rotation speed. Power ⁇ At a certain rotation speed, the efficiency decreases.
- This variable-diameter bury is provided with a number of belt engaging rods arranged in a circular pattern around a rotation axis and elastically attached radially outward by a biasing means.
- the diameter is the effective diameter of the variable diameter pulley.
- the effective radius of the variable-diameter pulley (that is, the contact radius of the belt) is reduced by moving the plurality of belt engaging rods radially inward against the urging force of the urging means. It is being changed.
- a plurality of spiral grooves extending in opposite directions to each other are formed in a pair of rotating plates facing each other, and both ends of the belt engaging rod are formed by the corresponding radial grooves of both rotating plates.
- Each part is supported.
- the effective diameter of each belt engaging rod can be changed with the relative rotation of the two rotating plates while maintaining the circular pattern arrangement.
- the urging means is between the two rotating plates.
- a torsion coil spring is used to urge both rotating plates in a direction to increase the effective diameter.
- variable diameter bury disclosed in the above-mentioned publication employs the above-mentioned large number of belt engaging rods and has a large number of parts.
- the belt engaging rods are arranged in a circular pattern to form a circular pattern.
- the disadvantage is that the diameter must be changed, which complicates the structure.
- the diameter of the above-mentioned circular pattern is such that the belt pushes the belt engaging rod inward in the radial direction and the biasing force of the torsion coil spring as biasing means balances the radial direction of the belt engaging rod.
- the effective diameter of the variable diameter pulley may fluctuate sensitively to torque fluctuations and the like. To prevent this, it is conceivable to increase the urging force. However, in this case, the friction torque increases, impairing the smoothness of shifting, and increasing the loss of transmission torque.
- an object of the present invention is to provide a variable-diameter bury which has a simple structure, can smoothly shift, and is insensitive to torque fluctuation.
- a variable-diameter bury capable of changing an effective radius of a wound belt is provided so as to surround a circumference of a rotary shaft that is rotated in a predetermined rotation direction.
- a pair of second connecting means connected to each other, wherein the pair of second connecting means correspond to each other so as to bring the pair of bully bodies closer to each other with an equal stroke amount. It is characterized by including a pair of conversion mechanisms for converting the relative rotation between the main body and the rotary shaft into the axial movement of the corresponding pulley main body.
- the transmission torque force conversion mechanism converts the force into a force for bringing both pulley main bodies closer to each other, adds the force to the urging force by the urging means, and balances the force for moving the pulley away. Therefore, even if there is a torque fluctuation below a certain level, the effective radius of the variable diameter pulley does not change.
- the belt was supported by using a plurality of belt engaging rods, so that there was a problem that the structure was complicated and the number of frictional portions increased in the portion for supporting the belt. Since a pair of annular pulley bodies are used as means for supporting the belt, the number of parts is small, the structure is simple, and the number of friction points is large.
- the conversion mechanism brings the two bridge bodies closer to each other with an equal stroke amount, even if the effective radius of the variable diameter pulley changes, the center of the belt in the ⁇ direction (the direction orthogonal to the running direction) is maintained. The position does not change.
- the tapered torque transmitting surface is a concept including not only a straight diagonal inclined surface but also a curved inclined surface.
- the first connecting means includes a fitting protrusion and a fitting recess formed respectively on each pulley main body, and a fitting protrusion and a fitting recess of one pulley main body. Are fitted into the other bully-based fitting recess and fitting projection, respectively.
- each bully body also serves as a connecting means, the number of parts can be reduced and the structure can be simplified as compared with a case where this is separately configured.
- an annular power transmission body having a belt wound around the outer peripheral surface thereof, wherein the power transmission body can be eccentric with respect to the shaft center of the pair of pulleys. And a pair of torque transmission surfaces, and torque is transmitted between the belt and the pair of buries via the power transmission body.
- the belt instead of a V belt as the belt.
- a different material from the belt can be selected as the power transmission body.
- resin can be used for the power transmission body.
- the power transmission body is made of resin, it is difficult to seize the main body of the pulley, and the coefficient of friction with the main body of the pulley can be increased.
- the inertial member further include an inertial member that is relatively displaced in relation to the power transmission body and an elastic support unit that elastically supports the inertial member on the power transmission body.
- the inertia and elastic support means function as a dynamic damper for reducing the vibration of the power transmission body, so that the vibration of the power transmission body can be greatly reduced.
- the elastic supporting means a fluid such as oil or grease having dead elasticity can be used in addition to an elastic member made of rubber, resin and metal.
- the urging means is formed of an elastic member housed in a housing space formed between the pair of pulley bodies and the rotating shaft.
- the size of the elastic member can be reduced as compared with the case where the elastic member as the urging means is arranged on the side of the bridge.
- the pulley is mainly used, it is difficult for dust or water to enter from outside, so that deterioration of the elastic member can be prevented.
- the pair of pulley main bodies each include a pair of portions extending to the other back side, and the elastic member connects the pair of portions extending to the back side to each other. It is preferable that the pair of pulleys be urged toward the side closer to each other by being pushed in the separating direction.
- both pulley main bodies can be uniformly pushed with the same force. Therefore, the force with which both bully bodies sandwich the belt or the power transmission body can be made uniform. Also, make the sum of the stroke amount of the elastic material and the stroke amount of both pulleys equal.
- the force of the elastic member can be reduced to half compared with the case where the elastic member pushes only the main pulley. Therefore, the size of the elastic member can be further reduced.
- FIG. 1 is a longitudinal sectional view of a variable-diameter bully according to a first embodiment of the present invention, and shows a state where a maximum contact diameter is reached.
- FIG. 2 is a schematic diagram of a belt transmission for driving an engine accessory using the variable diameter pulley of FIG.
- FIG. 3 is a diagram showing the relationship between the engine speed and the speed of the auxiliary equipment.
- FIG. 4 is a longitudinal sectional view of a variable diameter bridge having an intermediate contact diameter between the maximum and the minimum.
- Fig. 5 is a front view mainly showing the buries.
- FIG. 6 is a longitudinal sectional view of a variable-diameter bury according to a second embodiment of the present invention.
- FIG. 7 is a side view of the variable diameter bury of FIG.
- FIG. 8A and 8B are schematic cross-sectional views of main parts of a variable diameter bridge as a third embodiment of the present invention.
- FIG. 8A shows a state where the maximum contact diameter is reached.
- B shows the state where the minimum contact diameter is reached.
- FIG. 9 is a diagram showing the relationship between the distance between the two bridge bodies and the contact diameter in the embodiment of FIG.
- FIG. 10 is a cross-sectional view of a power transmission ring of a variable speed bury according to a fourth embodiment of the present invention.
- FIG. 11 is a longitudinal sectional view of a variable diameter pulley according to a fifth embodiment of the present invention, showing a state where the effective radius becomes the maximum.
- FIG. 12 is a half side view of the variable diameter bury of FIG.
- FIG. 13 is an exploded perspective view of the pulley main body and the guide member of the variable diameter pulley of FIG. 11 o
- FIG. 14 is an exploded perspective view showing a state in which the guide member is fitted on the outer peripheral surface of the bulge-based fitting projection of the variable diameter bury of FIG.
- FIG. 15 is a partially cutaway perspective view of the guide member of the variable diameter bury of FIG.
- FIG. 16 is a perspective view showing a state where a guide member and a link rest are combined with a fitting protrusion mainly composed of a pulley of the variable diameter pulley of FIG. 11.
- FIG. 17 is an exploded perspective view showing a state R in which a connecting body is combined with two bridge main bodies combined with each other of the variable diameter pulley of FIG. 11.
- FIG. 18 is an enlarged sectional view of a portion near the inner periphery of the variable diameter pulley of FIG.
- FIG. 19 is an exploded perspective view of the connection body of the variable diameter pulley and the rotation shaft of FIG.
- FIG. 20 is a schematic vertical cross-sectional view showing a profile in which the variable diameter burry of FIG. 11 has a minimum effective radius.
- FIG. 2 is an overall schematic diagram of S.
- auxiliary equipment is presented here only as a specific example, but for example, an air pump 3, an alternator 4, an air conditioner compressor 5, a power steering pump 6, and a war pump 7 etc. All of which are driven by a variable diameter pulley 8 connected to the engine crankshaft.
- the tensioner 200 described above is conceptually schematically shown in FIG.
- An idler pulley 9 is interposed between both the pulley of the alternator 4 and the pulley of the air conditioner compressor 5, and the idler pulley 9 is used to wind the belt 2 around the pulleys. Suitable hanging angle (contact angle) In some cases, adjustment to an appropriate size is performed.
- the tensioner pulley 10 is provided so as to be displaceable, and is displaced by a hydraulic cylinder 260 between a first position indicated by a solid line and a second position indicated by a broken line in FIG. You.
- the variable diameter pulley 8 has a maximum contact radius (maximum effective radius) with respect to the belt 2 corresponding to the first position, and the variable diameter pulley 8 has a minimum contact radius with respect to the second position S. (Minimum effective radius).
- the power transmission ring 20 is eccentric with respect to the center of the variable diameter pulley 8 as indicated by Di. The concepts of contact radius and effective radius will be described in detail later.
- a continuously variable transmission is achieved by setting the contact radius (effective radius) between the maximum and the minimum as desired.
- the displacement position of the tensioner pulley 10 may be set in advance to a plurality of stages, and a plurality of stages of shifting may be performed according to the plurality of stages of displacement.
- the controller 12 includes an output signal of a first speed sensor 13 as a state-of-depression detecting means for detecting the rotational speed of the variable-diameter pulley 8 and a state-quantity detecting means for detecting the rotational speed of the idler pulley 9.
- the output signal of the second speed sensor 14 is input.
- the rotation speed of the variable-diameter pulley 8 is equal to the engine rotation speed, and the rotation speed of the idle pulley 9 corresponds to the running speed of the belt 2.
- the output signal from the first speed sensor 13 is input to detect the engine speed, for example, when the engine speed is lower than a predetermined level, the first position is detected.
- the revolution speed of the auxiliary machine is made relatively higher than the engine revolution speed, and it is displaced to the second position when the engine revolution speed is equal to or higher than a predetermined level. This makes it possible to make the rotation speed of the accessory relatively lower than the rotation speed of the engine.
- the controller 12 detects the traveling speed of the belt 2 based on the input of the output signal from the second speed sensor 14, and controls the traveling speed to be a predetermined ratio with respect to the engine speed. Adjust the amount of displacement of the tensioner pulley 10 by the hydraulic cylinder 2 G 0. This is the long term The speed ratio may deviate from the initially set value due to the elongation of the belt 2 due to the use of the belt, so that this is prevented and the change ratio is maintained at the initially set value.
- variable-diameter pulley 8 includes: (1) a commercial rotary shaft 15 coaxially rotatable integrally with the crankshaft of the engine; First and second pulley bodies screw-fitted and integrally rotatably connected to first and second screw portions 16, 17 formed with opposite screws and at the same pitch, respectively. 18. 19, 3 Fitted in V groove 21 defined between both pulley main bodies 18, 19, and eccentric with respect to axis Di 15 a of rotary shaft 15 as shown in Fig. 4
- a power transmission ring 20 (hereinafter also referred to as an eccentric ring 20) as a possible power transmission body, and the first pulley main body 18 is biased in a direction in which the main pulley main bodies 18 and 19 approach each other.
- An annular disc spring 22 as an urging means is provided as a main part.
- the inner circumference of the plate 22 is supported by a support ring 25 fitted around the rotation 1 15, and its movement in the axial direction is restricted.
- the belt 2 is a flat belt provided with, for example, a V-shaped rib to secure a contact surface on its inner peripheral surface.
- the eccentric ring 20 has an annular shape with a trapezoidal cross section, and has a transmission surface 20a for the belt 2 formed on the outer peripheral surface. A circumferential groove is formed on the power transmission surface 20 a so as to engage with the rib of the belt 2.
- the contact radius D is defined by the radial center of the area where the torque transmitting surface 18 a .19 a is in contact with each side of the corresponding power transmission ring 20 and the axis di 15 a of the rotating shaft 15. It is separation.
- the effective radius S is the distance between the inner peripheral surface of the belt 2 located radially outward of the contact area and the axis Di 15 a of the rotating shaft 15.
- the cylindrical rotary shaft 15 is fastened to the crankshaft 23 via bolts 24.
- Reference numeral 26 denotes a key for connecting the mounting 23 and the rotating shaft i5 so as to be integrally rotatable.
- the first male screw portion 16 is disposed closer to the engine than the second male screw portion 17. Assuming that the shaft 15 is rotating around its axis 15a in the direction indicated by the arrow X in the figure, the first male screw is parallel to the rotation axis 15a and viewed in the Y direction.
- the portion 16 is a right-hand thread (which is screwed into the first pulley main body 18 by rotating in the anti-X direction), and the second male thread portion 17 is a left-hand thread (rotate in the X direction). Especially From the second pulley main body 19).
- the attachment of the disc spring 22 that pushes the first pulley main body 18 along the Y direction is as follows.
- the pulleys 18 and 19 are rotated in the anti-X direction with respect to the rotation axis 15 so that the pulleys 18 and 19 are brought closer to each other by an equal distance ft.
- the main pulleys 18 and 19 are rotated in the X direction with respect to the rotary shaft 15 and the main pulleys 18 and 19 with respect to the rotary shaft 15, the two main pulleys 18 and 19 are equal to each other only by S3 ⁇ 4. They will move away (see Figures 1 and 4).
- both pulley main bodies 18 and 19 are formed in substantially the same shape, the first pulley main body 18 has a force ⁇ , and an annular convex portion 1 that can engage the outer periphery of the disc spring 22. The only difference is that they have 8 1.
- the first boogie main body 18 has: 1) a tapered surface as a torque transmitting surface for defining the V groove 21.
- a main part 18 b composed of a circular annular plate having 18 a; and a plurality of fitting projections 18 c extending in the axial direction from the main part 18 b and arranged at equal circumferences.
- 3 »Mating is formed between the mating projections 18 c that are in contact with each other, and is an annular fitting groove 18 d that is open inward in the annular shape. 4Mates on the inner peripheral side of the main portion 18 b
- a first female thread 18 e is formed on the base end side of the projection 18 c and engages with the first male thread 16.
- the second bridge main body 19 includes a main body 19 b having a teno as a torque transmission surface and a surface 19 a, a plurality of fitting protrusions 19 c, and a fitting groove 1. 9 d, and a second female screw portion 19 e that meshes with the second male screw portion 17.
- the fitting projection 18 C of the first pulley main body 18 is fitted into the fitting groove 19 d of the second pulley main body 19, while the mating projection of the second pulley main body 19 is fitted.
- the 19 c force is fitted into the fitting groove 18 d of the first pulley main body 18.
- the outer peripheral surfaces of the fitting projections 18 c, 19 c of each pulley main body 18, 19 are in contact with the inner surfaces of the fitting grooves 19 d, 18 d of the other pulley main bodies 19, 18.
- the two pulley bodies 18 and 19 support each other so as to be rotatable and movable in the axial direction.
- the two pulley main bodies 18 and 19 are integrated by these fitting projections 18 c 1 9 (! And fitting groove 18 (1 and 19 d).
- First connecting means for connecting rotatably and movably relative to each other in the axial direction is configured. Since the pulley bodies 18 and 19 also serve as the first connecting means, the number of parts can be reduced and the structure can be simplified.
- a screw coupling mechanism including the second male screw portion 17 and the second female screw portion 19e is provided. Each of them is formed by a second means.
- Each screw coupling mechanism constitutes a converter (hereinafter, also referred to as a torque cam mechanism T). Since the two-screw coupling mechanisms are reverse-threaded to each other, when the two pulley bodies 18, 19, which are cultivated integrally, are relatively rotated with respect to the rotation shaft 15, the two pulley bodies 18, 19 are equally spaced from each other. It works so that only the noises come close or separate. Therefore, even if the contact radius changes, the center position of the belt 2 in the width direction does not change.
- the load torque is such that the pulley main bodies 18 and 19 are rotated in the anti-rotation direction (anti-X direction) with respect to the rotation shaft 15.
- This is the force that tries to shift the phase.
- the force for shifting the phase is converted by the torque cam mechanism T composed of the above-mentioned screw coupling mechanism, and becomes a force for bringing the two pulley main bodies 18 and 19 closer to each other.
- the eccentric ring 20 corresponding to the tension side portion of the belt 2 is attached to the two bulging bodies 1 Attempts to widen the distance between 8 and 19 and to enter the radially inward bulge 8 radially inward, but this is caused by the urging force of the disc spring 22 and the eccentric ring 20
- the load torque can be reduced by the force in the direction in which the eccentric ring '20 is displaced radially outward of the variable diameter pulley 8.
- the conversion efficiency depends on the inclination angles of the tapered surfaces 18a and 19a, the coefficient of friction between the eccentric ring 20 and the tapered surfaces 18a and 19a, and the screw coupling mechanism that constitutes the torque cam mechanism T.
- screw efficiency etc. it is possible to adjust in advance the limit value of up to how much tension of the eccentric 2 can resist the radially inward displacement of the eccentric ring 20. Then, beyond this limit value, the contact radius of the variable diameter pulley 8 is changed by the auto tensioner 10 increasing the belt tension.
- the above screw efficiency setting can be easily adjusted by setting the screw lead angle (for example, 45).
- the load torque is larger, the force for bringing both pulley main bodies 18 and 19 closer to each other can be increased, and the eccentric ring 20 can be strongly clamped.
- the occurrence of slip between the main bodies 18 and 19 can be prevented, and transmission loss due to the slip can be eliminated.
- the opposing force can be generated according to the load torque as described above, the urging force of the disc spring 22 can be kept small, so that the frictional force of the transmission torque can be reduced.
- the horizontal structure can be simplified as compared with the case where a large number of conventional belt engaging rods are used. Miniaturization can be achieved.
- the friction can be reduced, so that the frictional resistance can be reduced and the friction loss due to the urging force of the disc spring 22 can be reduced. Thus, a smoother shift can be achieved.
- FIG. 6 and 7 show a second embodiment of the present invention. Referring to these figures, this embodiment is mainly different from the first embodiment in that:
- first connecting means for connecting the first and second pulley bodies 27 and 28 so as to be integrally rotatable ffi bolts 29 and each bolt passing through both pulley bodies 27 and 28 are provided.
- nuts 30 that are fastened to each of the 29 top cities, (2) that each pulley main body 27, 28 is supported on the rotating shaft 15 via bushes 31, 32, respectively;
- a pair of countersunk springs 3 3 and 3 4 are provided to urge both pulleys 2 7. 2 8 in directions approaching each other.
- the pulley main bodies 27 and 28 have the same shape, and are arranged only in different directions.
- the first bridge main body 27 includes: (1) a main body part 27 b made of a circular annular plate having a tapered surface 27 a as a torque transmission surface for defining the V-groove 21; A cylindrical portion 27c formed concentrically with the main portion 27b in connection with the inner periphery of 27b, and 3 provided on the inner periphery of the quotient portion 27C, and the bush 31 is press-fitted.
- a plurality of the fitting concave portions 27 d, a first female thread 27 e formed on the inner periphery of the cylindrical portion 27 c, and a plurality of It has a bolt ⁇ through hole 27 f that penetrates in the axial direction a cylindrical portion 27 c through which each of the bolts 29 passes.
- the second pulley main body 28 includes a main body 28 having a tapered surface 28 a as a torque transmitting surface, a mouth-shaped portion 28 c, a fitting concave portion 28 d, It has a screw portion 28e and a bolt hole 28f.
- the rotating shaft 15 has a finger-moving surface 15b formed between the first and second externally threaded portions 16 and 17 and having a circumferential surface for sliding contact with the bush 31.
- the bolt 29 has a head 29 a, a long cylindrical body portion 29 b having no screw formed, and a screw portion 29 c, and the screw portion 29 c has:
- the nut 30 and the lock nut 35 are screwed.
- support rings 36, 37 for supporting the inner peripheral edges of the respective disc springs 33, 34 are rotatably fitted to the body 29b. Therefore, the support ring 25 adopted in the first embodiment is stopped.
- One support ring 36 is stopped from moving in the axial direction by the head 29 a of the bolt 29, and the other support ring 37 is stopped from moving in the axial direction by the nut 30.
- a bush 38 is used to support the body 29c so that it can slide in the axial direction.
- the bush 38 is pressed into the through holes 27f, 28f of the pulley bodies 27, 28, respectively.
- Reference numeral 15c denotes a key groove for inserting a key 26 for key-connecting the rotating shaft 15 and the mounting member 24.
- reference numeral 39 denotes a disc spring 33 and 34. These are radially formed slits, and increase the flexibility of the disc springs 33, 34.
- Other configurations are the same as those in the embodiment of FIG. 1, and therefore, the same reference numerals are given to the drawings and the description thereof will be omitted.
- the second embodiment similarly to the first embodiment, it is possible to prevent a change in the contact radius of the variable diameter pulley 8 due to a change in the load torque.
- simplification and downsizing of the ffi structure can be achieved, and further, various effects can be obtained such that friction loss is reduced and a smoother shift is possible.
- FIGS. 8A and 8B show a main part of a variable diameter bury according to a third embodiment of the present invention.
- the main difference between the present embodiment and the embodiment of FIG. 1 is that the torque transmission surfaces of pulley bodies 40 and 41 for forming V-groove 50 are formed.
- 40 a and 41 a are concave curved surfaces
- both side surfaces 4 2 b of the eccentric ring 42 are convex surfaces. It is a curved surface.
- 4 2 a is a transmission surface to the flat belt 2.
- the contact radius D (the pulley main body 40, 4) (The distance from the center of rotation to the contact points P 1 and P 2) can be changed progressively, and as a result, the pulley main bodies 40 and 41 can be enlarged without increasing the size.
- a large gear ratio can be secured.
- the speed change ratio of 1.75 can be set to 2.
- the change in the contact radius can be increased as described above because the contact portion P1 of the eccentric ring 42 in the state of the maximum contact radius (see FIG. 8A) This is because the contact portion P 2 (see FIG. 8B) of the eccentric ring 42 having a contact radius can be displaced radially inward at a predetermined distance. That is, the eccentric ring can be displaced more inward in the direction of the pulleys 40, 41.
- the contact surface between the pulley main body and the eccentric ring is a linear inclined surface, the contact portion of the eccentric ring is constant regardless of the change of the contact radius.
- the curvature of the concave curved surface forming the above torque transmitting surfaces 40a, 1a is the same as the curvature of the convex curved surface forming each side surface 42b of the eccentric ring 42. It is good or not, and in any case, it suffices if the contact portion of the eccentric ring 42 can be changed.
- the curvature of the concave curved surface or the convex curved surface described above may be changed in two steps, but when the contact part moves at the joint of the two curvatures, the sense of discontinuity (so-called It is necessary to connect smoothly so as not to cause shock. It is preferable to adopt a single curvature because there is no possibility of causing a sense of discontinuity.
- FIG. 10 shows an eccentric ring according to a fourth embodiment of the variable diameter pulley of the present invention.
- the eccentric ring 4 2 having only the shape of the inner diameter portion is different from the eccentric ring 42 of the embodiment shown in FIGS. 8A and 8B.
- a dynamic damper 44 was installed to prevent vibration of the eccentric ring 43.
- the inner diameter portion of the eccentric ring 43 has a small diameter portion 43c and a pair of large diameter portions 43d sandwiching the small diameter portion 43c, and these small diameter portions 43c and a pair of large diameter portions 43d are respectively formed.
- the dynamic damper 44 is connected to the stepped end face 43 e that is in contact.
- the dynamic damper 44 includes: (1) an annular member 45 as a weight member having a predetermined mass (also referred to as a resentment member) disposed inside the small diameter portion 43c of the eccentric ring 43; By connecting each end surface 45a of the annular member 45 with the corresponding stepped end surface 43e, respectively, a pair of rings as elastic members supporting the annular member 45 elastically are provided. 4 and 6 are provided.
- the annular member 4 5 elastically supported by the pair of rubber plates 4 6 vibrates and displaces in a direction parallel to the axial direction of the eccentric ring 43 while deforming the rubber plate 46, thereby causing the vibration of the eccentric ring 43.
- Energy can be dissipated and the amplitude can be greatly reduced.
- side When the eccentric ring 43 is eccentrically displaced, only one radial side of the eccentric ring 43 is supported by the pulley main body 400.41, and the other side in the radial direction is free. 3 has a tendency to cause side-to-side vibration, but the use of the above-mentioned dynamic damper 4 4 can greatly reduce the vibration.
- the above-mentioned dynamic damper is limited to the above configuration.
- various known members may be employed as long as they include a weight member and an elastic member.
- a so-called viscous damper having a structure in which a ball serving as a weight member is accommodated in a recess formed in an eccentric ring, and the recess is filled with oil / grease having a predetermined viscous elasticity '14 as an elastic member and sealed. Can also be used.
- variable pulley as a fifth embodiment of the present invention will be described with reference to FIGS.
- variable diameter bridge 8 is composed of (1) a cylindrical rotating shaft 302 connected coaxially and integrally rotatable with an engine crankshaft 301; A pair of pulley main bodies 300, 306 connected rotatably with each other via a rotary shaft 302 and a pair of connecting bodies 300, 304, respectively, and connected so as to be integrally rotatable with each other; (3) Both pulleys: A power transmission ring (309) fitted in a V-groove (307) defined between the main body (305) and (306) and eccentric to the axis (308) of the rotating shaft (302). ⁇ A plurality of pairs as an elastic member for urging the two pulley bodies 300,306 through the connecting bodies 303,304 in a direction in which the two pulley bodies 300,306 approach each other. Annular disc spring 30.30.310 as a main part.
- the rotating shaft 302 is fastened to the crankshaft 301 via bolts 31, and the rotating shaft 302 rotates integrally with the crankshaft 301.
- the belt 2 is formed of a flat belt such as a so-called V-ribbed belt provided with, for example, a V-shaped or other mountain-shaped rib 2b extending in the traveling direction to secure a contact surface ⁇ on the inner peripheral surface 2a.
- the power transmission ring 309 has a trapezoidal cross section and has a ring shape, and a transmission surface 313 to the belt 2 is formed on the outer peripheral surface.
- On the transmission surface 3 13, a circumferential groove 3 14 is formed which meshes with the rib 2 b of the belt 2.
- the V-groove 307 is formed between the opposing surfaces 315, 316 of both pulley main bodies 305, 306.
- the opposing peripheral side surfaces 317 and 318 of the power transmission ring 309 come into contact with these opposing surfaces 315 and 316 to transmit power.
- pulley main body 3 05 has a circular annular main body 3 2 1 having an opposing surface 3 I 5 having a tapered surface for partitioning V * 3 07. are doing.
- a plurality of arc-shaped fitting projections 3222 extending in one direction in the axial direction (the other pulley main body 310 side) from the inner peripheral portion of the main body 3221 are formed at equal circumferential intervals.
- arc-shaped fitting grooves 323 are formed in a circumferentially equidistant manner so as to correspond between the fitting projections 3222 that are in contact with each other.
- the main body 3 21 has a cylindrical portion 3 2 4 formed on the surface opposite to the opposite surface 3 15.
- the two bridge bodies 300 and 306 have a symmetrical shape.
- the pulley main body 310 also has a main body part 3 21, a fitting protrusion 3 22, and a cylindrical part 3 24 similar to the pulley main body 300.
- a plurality of guide members 3 25 for guiding the axial displacement between the two pulley bodies 35.3.06 are provided on the circumference of the cylindrical portion 3 24. S have been. These guide members 3 25 are formed in an arc shape that covers the outer circumference of the fitting projections 3 22 of the corresponding pulley main bodies 3 05, 3 0 6, and a circular shape is formed on the inner peripheral surface of the cylindrical portion 3 2 4. It is fitted and held in a plurality of arcuate holding grooves 326 formed in a circumferentially equal pattern. As shown in FIG. 15, the guide member 3 25 is composed of a guide body 3 27 made of an arc-shaped plate having a small coefficient of friction, and a guide body 3 27 surrounding the edge of the guide body 3 27. And a seal member 328.
- a sliding member such as a cylindrical bushing may be provided as a guide member to guide the relative axial displacement between the two bully bodies 300 and 306.
- the lubrication filled inside the bushing In addition to the possibility that oil and grease may leak, the bush is also provided in a portion where there is no moving counterpart material, which has the disadvantage of wasting space and insufficient strength.
- an arc-shaped guide member 325 circumscribing each of the fitting projections 322 was provided.
- the lubricating oil or grease filled inside is as shown by arrow 329 in FIG.
- the sealing member 328 contacts the edge of each fitting projection 3 22 so as not to leak along the edge of each fitting projection 3 22 to the outside. Leakage of the lubricating oil and the like can be prevented.
- both pulley main bodies 30 5 and 30 6 make the fitting projections 3 2 2 of the two pulleys inadequate to the mating lugs 3 2 3 of the other party, and as a result, both pulley main bodies 305 and 306 are spline-coupled to each other so as to be able to rotate together while allowing relative movement in the axial direction.
- the fitting projections 3 2 2, 3 2 2 of the pulley main bodies 3 0 5, 3 0 6 constitute a portion extending to the rear side through the other pulley main bodies 3 0 6, 3 0 5.
- the first connecting means is constituted by the fitting projections 3 22 and the fitting grooves 3 2 3.
- the left pulley main body 310 is spline-coupled to the right connecting body 303 so as to be integrally rotatable.
- the pulley main body 304 on the right side is spline-engaged with the connecting body 304 on the left side so as to be integrally rotatable. That is, referring to FIG. 17, the coupling bodies 303 and 304 have a plurality of fitting projections 331 formed on the outer circumference of one end side of the cylindrical portion 330 at equal circumferential intervals. The spline connection is achieved by engaging the fitting projection 331 with the corresponding fitting projection 3222 of the pulley main body 300,306.
- each of the connecting bodies 303, 304 is formed by a stop ring 33, which is a snub ring locked on the inner peripheral surface of the fitting projection 32, of the pulley main body 105, 303. It is prevented from escaping in the axial direction.
- the stopper 333 is fitted in a groove formed on the inner peripheral surface of the fitting protrusion 332 of the pulley main body 305,306.
- the above-mentioned disc springs 310 and 310 are accommodated in the accommodation space 334. These present disc springs 310 and 310 are arranged concentrically with the rotating shaft 302.
- the outer periphery of the storage space 334 is defined by a pair of thin cylinders 335.336 as a pair of seal members that are fitted and fixed to the outer peripheral surfaces of the connecting bodies 303 and 304.
- These thin-walled cylinders 335 and 336 are assembled so as to be slidably overlapped with each other, and the amount of polymerization of each of the connected bodies 303 and 304 is reduced with the axial movement of the connected bodies. It comes to be variable ing.
- the thin circles 335 and 336 are made of a thin plate such as stainless steel.
- the housing space 334 is covered by the thin wall 335.336, it is possible to reliably prevent the lubricating oil and the like filled therein from leaking to the outside.
- the function of the seal member 328 described above can more reliably prevent leakage of lubricating oil and the like.
- the above-mentioned disc springs 310, 310 are arranged in opposite directions to each other, and urge both pulley main bodies 310, 306 in a direction away from each other via both connecting bodies 303, 304.
- each of the coupling bodies 303 and 304 is constantly pressed against the corresponding stop 333 by the urging force of the disc springs 310 and 310.
- each of the coupling bodies 303 and 304 moves integrally with the corresponding bury main body 306 and 305 while expanding and contracting the disc spring 310.10 in the axial direction.
- the amount of change in the width of the V-shaped groove 307 of both the boules 305, 306 and the total stroke amount of the plurality of disc springs 310.10 are equal to each other.
- each of the coupling bodies 303 and 304 is rotatably supported on the outer peripheral surface of the rotating shaft 302 via a sliding bearing 340 such as a metal bush. Further, each of the coupling bodies 303 and 304 is cam-coupled to the rotating shaft 302. That is, referring to FIG. 19, a plurality of fitting projections 332 are formed on the inner peripheral surface of each connecting body 303 and 304 in a circumferentially equidistant manner. Are respectively fitted in a plurality of fitting grooves 337 circumferentially arranged at both ends in the axial direction of the cylindrical rotary shaft 302.
- fitting projections 332 and fitting grooves 337 are in contact with each other by inclined cam surfaces 338 and 339 which engage with each other.
- the inclination direction of the drum surface 338 is set to be opposite to the rotation direction between the two connecting bodies 303 and 304 (similarly, the cam surfaces 339 of the fitting grooves 337 are also formed at both ends of the rotation shaft 302).
- the cam surfaces 339 of the fitting grooves 337 are also formed at both ends of the rotation shaft 302).
- the torque cam mechanism T is constituted by a pair of cam surfaces 338, 339 which respectively connect the above-mentioned connecting bodies 303.304 and the rotating shaft 302.
- the two bridge bodies 3 0 5, 3 0 6 become: It will be displaced in the axial direction so that they are close to each other or separated from each other by an equal distance.
- Each of the coupling bodies 303 and 304 and the corresponding torque cam mechanism T constitute second coupling means.
- variable-diameter pulley 8 Even if a force that attempts to reduce the effective radius due to the fluctuation of the load torque of the variable-diameter pulley 8 acts, a force opposing the force can be generated by the torque cam mechanism T. Therefore, the variable-diameter pulley 8 caused by the fluctuation of the load torque Can be prevented from changing the effective radius. Also, as the load torque is larger, the torque cam mechanism T increases the force for bringing the two pulley bodies 3 05, 3 06 closer to each other, so that the power transmission ring 3 09 can be more strongly held. It is possible to prevent the occurrence of slippage between the power transmission ring 309 and the main burries 310, 306, and to eliminate transmission loss caused by the slippage.
- the resisting force can be generated according to the load torque as described above, the biasing force of the disc spring 310.310 can be kept small, so that the friction loss of the transmission torque can be reduced. can do.
- the efficiency in converting the load torque into a force in the direction in which the power transmission ring 309 is displaced radially outward of the variable diameter pulley 8 is determined by the opposing surfaces 3 15, 3 as tapered surfaces.
- the storage provided inside the two pulleys 3 05 and 30 6 Since the disc springs 310 and 310 as three single members are arranged in the storage space 334, the size of the elastic member can be reduced as compared with the case where the elastic member is provided on one side of one of the buries. can do.
- the elastic member is a disc spring 310, 310 concentric with the rotating shaft 302, the elastic member can be further reduced in size, and furthermore, can be formed into a / J shape of the variable diameter pulley 8.
- the inside of the two pulleys 305 and 306 is hard to receive dust and water from the outside, the disc springs 310 and 310 are prevented from deteriorating and the durability is improved. Can be improved.
- the above-mentioned disc spring 3 0, 310 can be prevented from deteriorating, and the lubricating oil and the like filled inside can be reliably prevented from leaking to the outside.
- the two thin cylinders 33 5. 336 ensure the sealing performance by adjusting the amount of polymerization by sliding the overlapping part of each other, without hindering the relative movement of the two bully bodies 3 05 and 306 in the relative glaze direction. be able to.
- the disc springs 3 1 0, 3 1 0 push the two bridge main bodies 305, 306 the sum of the axial displacement amounts of the two bridge main bodies 305, 306 and the plurality of disc springs 3 1 0 As a result, the stroke amount of the entire 3110 can be made equal, and as a result, the stroke amount can be doubled as compared with the case where the elastic member pushes only the main body of the bridge from the outside. Therefore, the force of the elastic member is reduced to half, and the elastic member can be made smaller. As a result, the variable diameter burley 8 can be made even smaller.
- the inclination direction of the cam surface of the torque cam mechanism T is determined by the pulley main bodies 30 5 and 30 6. This is a direction in which the phase shift generated in the rotation direction with respect to the rotation axis 302 can be converted into a movement for bringing the two pulley bodies 30.5 and 30.6 closer to each other. In other words, when used on the drive side pulley, the direction of rotation is reversed.
- a screw mechanism as in the embodiment of FIG. 1 may be adopted as the torque cam mechanism.
- the dynamic damper of FIG. 10 according to the form of the third embodiment can be applied to the eccentric ring of the form of the embodiment of FIGS. 1, 6 and 1.
- a torque mechanism is configured.
- the direction of thread formation of the screw coupling mechanism is such that the phase shift of the pulley main body with respect to the rotation shaft 15 in the cultivation direction can be converted into a movement of bringing both burley main bodies close to each other.
- the direction of rotation is opposite to that in the case of using the pulley on the drive side.
- a compression coil spring concentric with the rotating shaft can be used as the elastic member instead of the disc spring.
- the eccentric ring may be omitted and the V-belt may be directly fitted to the V Marie
- the torque transmitting surface of the V-groove is formed into a concave curved surface, and both side surfaces of the V-belt are formed into convex curved surfaces.
- the size and the durability of the continuously variable transmission 1 can be improved by reducing the size and the durability of the variable pulley 8. Can be achieved.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmissions By Endless Flexible Members (AREA)
- Pulleys (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE69723237T DE69723237T2 (de) | 1996-03-08 | 1997-03-07 | Scheibe mit verstellbarem durchmesser |
EP97906853A EP0884504B1 (en) | 1996-03-08 | 1997-03-07 | Variable diameter pulley |
US09/142,378 US6129643A (en) | 1996-03-08 | 1997-03-07 | Variable diameter pulley |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP05192996A JP3660044B2 (ja) | 1995-07-19 | 1996-03-08 | 可変速プーリ |
JP8/51929 | 1996-03-08 | ||
JP02078197A JP3623334B2 (ja) | 1997-02-03 | 1997-02-03 | 可変径プーリ及びこれを含む無段変速機 |
JP9/20781 | 1997-02-03 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1997033105A1 true WO1997033105A1 (fr) | 1997-09-12 |
Family
ID=26357767
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1997/000713 WO1997033105A1 (fr) | 1996-03-08 | 1997-03-07 | Poulie a diametre variable |
Country Status (4)
Country | Link |
---|---|
US (1) | US6129643A (ja) |
EP (1) | EP0884504B1 (ja) |
DE (1) | DE69723237T2 (ja) |
WO (1) | WO1997033105A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
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WO1998041785A1 (en) * | 1997-03-15 | 1998-09-24 | Gkn Technology Limited | Rotary device of variable diameter |
FR2784157A1 (fr) * | 1998-10-02 | 2000-04-07 | Luk Lamellen & Kupplungsbau | Mecanisme a organe de transmission sans fin reglable en continu |
DE19881945B4 (de) * | 1997-11-13 | 2006-05-04 | Koyo Seiko Co., Ltd. | Riemen-System mit kontinuierlich variabler Drehzahl |
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US6585615B2 (en) * | 2000-02-17 | 2003-07-01 | Koyo Seiko Co., Ltd. | Power transmission ring and variable diameter pulley assembly using the same |
US6659894B2 (en) | 2001-07-12 | 2003-12-09 | Generac Power Systems, Inc. | Variable pitch sheave assembly for fan drive system |
US7033293B2 (en) * | 2002-08-22 | 2006-04-25 | The Gates Corporation | Expandable pulley |
WO2006087469A1 (fr) * | 2005-02-15 | 2006-08-24 | Aktiebolaget Skf | Dispositif de roulement codeur et machine tournante |
US20100016108A1 (en) * | 2005-12-10 | 2010-01-21 | Cvtron Ltd. | Transmission System Particularly Useful as a Continuously Variable Transmission |
FR2902699B1 (fr) * | 2006-06-26 | 2010-10-22 | Skf Ab | Dispositif de butee de suspension et jambe de force. |
FR2906587B1 (fr) * | 2006-10-03 | 2009-07-10 | Skf Ab | Dispositif de galet tendeur. |
FR2906858B1 (fr) * | 2006-10-04 | 2008-12-05 | Skf Ab | Dispositif de poulie debrayable. |
FR2910129B1 (fr) * | 2006-12-15 | 2009-07-10 | Skf Ab | Dispositif de palier a roulement instrumente |
FR2913081B1 (fr) * | 2007-02-27 | 2009-05-15 | Skf Ab | Dispositif de poulie debrayable |
DE102007062218A1 (de) | 2007-12-21 | 2009-06-25 | Mahle International Gmbh | Antriebsanordnung |
US8267835B2 (en) * | 2008-03-18 | 2012-09-18 | Briggs And Stratton Corporation | Generator set |
US8845486B2 (en) * | 2008-03-18 | 2014-09-30 | Briggs & Stratton Corporation | Transmission for outdoor power equipment |
US8932161B2 (en) | 2011-09-09 | 2015-01-13 | Chrysler Group Llc | Variable speed alternator |
EP2799309A4 (en) * | 2011-12-26 | 2015-05-06 | Toyota Motor Co Ltd | STEERING DEVICE WITH ELECTRICAL ASSISTANCE |
JP6257905B2 (ja) * | 2013-03-22 | 2018-01-10 | 株式会社豊田中央研究所 | 無段変速機 |
NL1040573C2 (en) * | 2013-12-24 | 2015-06-26 | Bosch Gmbh Robert | A continuously variable transmission with pulleys and a drive belt. |
JP6353974B2 (ja) * | 2015-04-06 | 2018-07-04 | 本田技研工業株式会社 | 無段変速機 |
JP6428733B2 (ja) * | 2016-09-13 | 2018-11-28 | トヨタ自動車株式会社 | 車両用チェーンベルト式無段変速機の制御装置 |
US10309531B2 (en) * | 2016-12-20 | 2019-06-04 | Ford Global Technologies, Llc | Continuous variable transmission with mechanical lock |
US10473195B2 (en) * | 2017-06-06 | 2019-11-12 | GM Global Technology Operations LLC | Continuously-variable transmission |
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Also Published As
Publication number | Publication date |
---|---|
DE69723237D1 (de) | 2003-08-07 |
DE69723237T2 (de) | 2004-05-27 |
EP0884504A1 (en) | 1998-12-16 |
EP0884504B1 (en) | 2003-07-02 |
US6129643A (en) | 2000-10-10 |
EP0884504A4 (en) | 2000-12-13 |
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