CN101283203A - Pulley apparatus and auto-tensioner - Google Patents

Abstract

A pulley apparatus and auto-tensioner which have a simple constitution and, despite this, can impart torsion-spring properties to an inner member and an outer member. Due to the torsion-spring properties, the fluctuations in tension, rotational speed, etc. of a belt stretched on a pulley part disposed on either of the inner member and the outer member can be effectively mitigated. The apparatus comprises an outer member having an outer track surface on the inner peripheral side thereof, an inner member which has, on the outer peripheral side, an inner track surface facing the outer track surface and which is disposed so as to be rotatable relative to the outer member, and rolling elements rollably interposed between the outer track surface and the inner track surface. At least one of the inner track surface and the outer track surface has, in at least part thereof, a different-shape track surface which serves to gradually narrow the space where the rolling elements are sandwiched and which imparts a rotational force in such a direction that a phase difference generated between the outer member and the inner member as a result of the relative rotation of the outer member and the inner member is eliminated, while allowing the rolling elements to roll with the relative rotation.

Description

Pulley apparatus and automatic takeup

Technical field

The present invention relates to pulley apparatus and automatic takeup.

Background technique

The subsidiary engine class of the motor of automobile etc. is power-actuated by the rotation of the bent axle of being exported by the driving mechanism that has used belt.Volume is hung in the pulley apparatus of belt in this driving mechanism, the pulley apparatus that is installed on the bent axle on the bent axle and uses is arranged, be installed on pulley apparatus that the alternator on the alternator uses, have the automatic takeup that is used for the tension force of above-mentioned belt is kept certain belt pulley.

The bent axle of the generator of the pulley apparatus that above-mentioned bent axle uses is installed,, therefore can in its rotating speed, produces change owing to be to give rotating force by the explosive force of cylinder.In addition, in case the change of the rotating speed of this kind bent axle is passed to the subsidiary engine class via belt, then the subsidiary engine class that produces inertial force because of rotation just can't be followed the change of this rotating speed.Therefore, just have the overtension ground change of belt, the situation of generation slippage between pulley apparatus and belt.The excessive change of the slippage of this kind belt or tension force becomes the reason that the generation of abnormal noise of belt or life-span reduce etc.In addition, in order to prevent the slippage of belt, set the initial tension of this belt than higher sometimes, under this situation, the rotational resistance of bent axle increases, thereby has the situation of the oil consumption performance that reduces generator.

In addition, because bent axle itself is not to form axisymmetrically in the axial direction, therefore the change of the rotating speed of above-mentioned bent axle also can become the reason of the torsional vibration of bent axle itself or the vibration that rises and falls.

For this reason, for example described in TOHKEMY 2003-172403 communique, in order to alleviate the influence that causes by the change of the rotating speed of bent axle, propose to have to possess to other parts: be installed on belt pulley hub on the bent axle, the periphery volume hang the tubular of belt the belt pulley member, be located in the bent axle pulley apparatus of the vibration isolation rubber between above-mentioned belt pulley hub and the above-mentioned belt pulley member.This kind pulley apparatus will be by being located in by the vibration isolation rubber that elastomer is made between belt pulley member and the bent axle, and make both flexibly rotations relatively along the circumferential direction, and the belt pulley member is played a role as the vibration damping material at bent axle, and obtain damping effect.Utilize this damping effect, absorb the vibration of bent axle, and alleviate the rotating speed change of bent axle.

Utilize the damping effect of that above-mentioned bent axle in the past obtains with pulley apparatus, as to be used to alleviate bent axle rotating speed change to depend on the elastic characteristic of vibration isolation rubber greatly.Though the elastic characteristic of vibration isolation rubber can change by elastomeric material, its thickness size that change to constitute this vibration isolation rubber, yet utilize the modifiable scope of the elastic characteristic that this kind method obtains not too wide, its degrees of freedom is low.Thereby, utilize above-mentioned pulley apparatus in the past, can't suitably set the elastic characteristic of vibration isolation rubber sometimes, can't alleviate the vibration or the rotating speed change of bent axle effectively.

In addition, be equipped with in the alternator of the pulley apparatus that alternator uses, the input shaft of the pulley apparatus of using at bigger armature of weight inside etc. and this alternator rotates integratedly, as mentioned above, when the change of the rotating speed of bent axle is very fierce, have the inertial force that the rotation of armature reason self produces, and can't follow the situation of change of the rotating speed of bent axle.If alternator can't be followed the change of above-mentioned rotating speed, then can between the rotating speed of bent axle and alternator, temporarily produce difference aspect the rotating speed, thus the situation that has the overtension ground that between pulley apparatus and belt, produces slippage, belt to change.The excessive change of the slippage of this kind belt or tension force can become the reason that the generation of abnormal noise of belt or life-span reduce etc.And, in order to prevent the slippage of belt, to set the initial tension of this belt than higher sometimes, under this situation, the rotational resistance of bent axle increases, thereby also has the situation of the oil consumption performance that reduces motor.

For this reason, for example described in the flat 6-207525 communique of TOHKEMY, in the pulley apparatus that alternator is used, in order to allow the change of the rotating speed that transmits by bent axle, proposed to have: outer circumferential face be provided with that volume is hung the belt pulley member of the pulley groove of belt, quilt is set with respect to this belt pulley member with rotating freely and can and the input shaft of alternator integratedly rotatably the belt pulley hub of installation, link between with above-mentioned belt pulley member and above-mentioned belt pulley hub turned round helical spring device.In the pulley apparatus that above-mentioned alternator is in the past used, turned round helical spring and constituted, the one end is fixed on the belt pulley member, the other end is fixed on the belt pulley hub, thereby in that the belt pulley member is relative with belt pulley hub when rotating, this is turned round helical spring and can be reversed.Like this, reversed the elastic force that produces because of turning round helical spring, temporarily made the along the circumferential direction flexibly relative rotation of belt pulley member and belt pulley hub, alleviated the change of rotating speed by utilizing.

The pulley apparatus used of alternator according to above-mentioned example in the past, the belt pulley member depends on the above-mentioned helical spring of being turned round with respect to the alleviation characteristic of the rotation change of belt pulley hub, yet because this is turned round the restriction of size that helical spring is subjected to being encased in the degree of this pulley apparatus, therefore its line footpath or free length, the number of turns etc. are restricted, and can't freely set and be turned round helical spring characteristic.Therefore, the degrees of freedom in the alleviation characteristic of the rotation change of setting the pulley apparatus of using as alternator is restricted, and might alleviate the rotating speed change of bent axle fully.

As mentioned above, the pulley apparatus that pulley apparatus that utilization bent axle is in the past used and alternator are used can't be alleviated the rotating speed change of bent axle sometimes fully.

In addition, used automatic takeup in the above-mentioned driving mechanism, for example described in the flat 7-4481 communique of TOHKEMY, can be the front end of the swing arm of center swing with the support that is fixed on the motor etc., have volume and hang up the belt pulley of stating belt, swing arm can utilize by being installed on the elastic force of being turned round the helical spring generation between this swing arm and the support and flexibly swing.This kind automatic takeup is by giving certain force of strain along the swaying direction application of force of stipulating to belt with belt pulley.In addition, can utilize simultaneously the flexible swing of swing arm to absorb the tension change of the belt that produces because of the rotating speed change of motor etc., prevent the vibration of belt or the generation of abnormal noise, guarantee the life-span that belt is original.In addition, can absorb fluctuation by the length of the alignment error of subsidiary engine, dimensional changes that temperature variation causes or belt etc.

According to the above-mentioned automatic takeup of example in the past, the change absorption characteristic of the belt tension of swing arm depends on the above-mentioned helical spring of being turned round, yet because this is turned round the restriction that helical spring is subjected to the size of the degree in this automatic takeup that can be encased in, therefore its line footpath or free length, the number of turns etc. are restricted, and can't freely set the characteristic of being turned round helical spring elastic force.Therefore, can be restricted as the degrees of freedom in the change absorption characteristic of the belt tension of automatic takeup, can't absorb the change of belt tension sometimes fully in setting.

Summary of the invention

Given this present invention plants situation and finishes, and its purpose is, the pulley apparatus and the automatic takeup of the change of the rotating speed change that can alleviate, absorb bent axle effectively or belt tension is provided.

The present invention is the pulley apparatus that is used for driving by belt the subsidiary engine class of motor, it is characterized in that possessing: roll up the belt pulley member cylindraceous of hanging belt and having the outboard raceway face in interior all sides in periphery; Have and the opposed inboard raceways face of above-mentioned outboard raceway face at outer circumferential side, and be adapted to can be with respect to the counterrotating inner member of above-mentioned belt pulley member; Rollably be located in the rolling element between above-mentioned outboard raceway face and the above-mentioned inboard raceways face, at least one side of above-mentioned inboard raceways face and outboard raceway face has special-shaped roller surface at least a portion, this abnormity roller surface is on one side along with above-mentioned belt pulley member makes the rolling element rolling with relative rotation between the above-mentioned inner member, reduce the clamping interval of this rolling element on one side gradually, and to giving rotary action power between above-mentioned belt pulley member and the above-mentioned inner member, this rotary action power is to eliminate the power of the direction of the above-mentioned belt pulley member that produces because of above-mentioned relative rotation and the phase difference between the above-mentioned inner member.

Pulley apparatus according to constituting does not as described above use and is turned round helical spring etc., can enough simple formations to giving rotation urging function (below be also referred to as torsion spring) between belt pulley member and the inner member.That is, utilize this torsion spring, relatively rotate with can making two component elasticities, mitigation is in the tension change of the belt of belt pulley portion, rotating speed change etc. effectively.In addition, the shape by changing special-shaped roller surface or the external diameter of rolling element etc. can make and utilize the characteristic of the torsion spring that above-mentioned formation obtains diversely to change, and make the degrees of freedom of its setting become high.

Above-mentioned pulley apparatus also can be by on the input shaft that but above-mentioned inner member one is installed on rotatably alternator and use as the pulley apparatus that alternator is used.

Under this situation, utilize above-mentioned torsion spring, the along the circumferential direction flexibly relative rotation of belt pulley member and input shaft can be able to be alleviated the change of the rotating speed that is caused by bent axle, and transmit rotating force to the input shaft of alternator.In addition, the shape by changing special-shaped roller surface or external diameter of rolling element etc. can make and utilize the characteristic of the torsion spring that above-mentioned formation obtains diversely to change, and make the degrees of freedom of its setting become high.Thereby, can give suitable elastic force characteristic to pulley apparatus according to the specification of the alternator that the pulley apparatus that this alternator uses is installed or characteristic of motor etc.

In addition, but above-mentioned pulley apparatus also can be and use as the pulley apparatus that bent axle is used by above-mentioned inner member one being installed on rotatably on the bent axle.

Under this situation, utilize above-mentioned torsion spring, can make the along the circumferential direction flexibly relative rotation of belt pulley member and bent axle, can make the belt pulley member alleviate the vibration of bent axle as playing a role thus, and alleviate the rotating speed change of bent axle at the vibration damping material of bent axle.

In addition, the shape by changing special-shaped roller surface or the external diameter of rolling element etc. can make and utilize the characteristic of the torsion spring that above-mentioned formation obtains diversely to change, and make the degrees of freedom of its setting become high.Thereby, can give suitable elastic force characteristic to pulley apparatus according to the specification of the motor that this pulley apparatus is installed or characteristic etc.

In the above-mentioned pulley apparatus, be preferably between above-mentioned belt pulley member and the above-mentioned inner member, be folded with the rolling bearing that they are supported mutually with one heart.

Under this situation,, therefore can reduce the load load that acts on special-shaped roller surface and the rolling element from the outside owing to can utilize above-mentioned rolling bearing to come the load load radially of supporting role on above-mentioned belt pulley member.Thereby can more stably obtain above-mentioned torsion spring.

In addition, the feature of automatic takeup of the present invention is to possess: swing arm, its have interior all sides be formed with the tubular of outboard raceway face base end part, and extend and the belt pulley that will roll up the extension belt is fixed into the arm that rotates freely from this base end part; Support member, it has and the opposed inboard raceways face of above-mentioned outboard raceway face at outer circumferential side, comes the above-mentioned swing arm of free swaying ground supporting by supporting above-mentioned base end part with the relative rotation; Rolling element, it rollably is located between above-mentioned outboard raceway face and the above-mentioned inboard raceways face, and, at least one side of above-mentioned inboard raceways face and outboard raceway face has special-shaped roller surface at least a portion, this abnormity roller surface is on one side along with above-mentioned base end part makes the rolling element rolling with relative rotation between the above-mentioned support member, reduce the clamping interval of this rolling element on one side gradually, and to the rotary action power of the direction of giving above-mentioned base end part that elimination produces because of above-mentioned relative rotation and the phase difference between the above-mentioned support member between above-mentioned base end part and the above-mentioned support member, utilize this rotary action power, with the swaying direction application of force of above-mentioned swing arm to regulation.

Automatic takeup according to constituting does not as described above use and is turned round helical spring etc., and the enough simple formations of energy are to giving the rotation urging function between base end part and the support member.That is, can utilize this torsion spring, swing arm is flexibly swung, the swaying direction application of force of above-mentioned swing arm to regulation.Can give tension force to the belt that volume hangs on the belt pulley thus.In addition, the shape by changing special-shaped roller surface or the external diameter of rolling element etc. can make and utilize the characteristic of the torsion spring that above-mentioned formation obtains diversely to change, and make the degrees of freedom of its setting become high.Thereby, can be according to the characteristic of motor or specification etc., set the elastic force characteristic in the swing arm swing rightly.

In addition, in above-mentioned automatic takeup, be preferably between above-mentioned base end part and the above-mentioned support member, be folded with the rolling bearing that they can be supported mutually with the relative rotation.

Under this situation,, therefore can reduce the load load that acts on special-shaped roller surface and the rolling element from the outside owing to can utilize above-mentioned rolling bearing to come the load load radially of supporting role in above-mentioned base end part.Thereby, can more stably obtain above-mentioned torsion spring.

Description of drawings

Fig. 1 is the axial sectional view of wanting portion's formation of the pulley apparatus used as the alternator of first mode of execution of the present invention of expression.

Fig. 2 is the sectional view of II-II line among Fig. 1.

Fig. 3 is the sectional view that is used to illustrate the rotary action power that produces because of belt pulley hub and relative rotation between the belt pulley member.

Fig. 4 is the sectional view as the pulley apparatus of second mode of execution of the present invention.

Fig. 5 is the sectional view that is used for illustrating in the rotary action power that produces because of belt pulley hub and relative rotation between the belt pulley member according to the pulley apparatus of second mode of execution.

Fig. 6 is the plotted curve of the rotating speed of the expression timeliness of having measured the rotating speed of belt pulley member, axle and the result's of timeliness a example.

Fig. 7 be amplitude h in the presentation graphs 6 and amplitude i, and the frequency of the cyclical swing of the rotating speed of belt pulley member between the plotted curve of relation.

Fig. 8 is the axial sectional view of wanting portion's formation of the pulley apparatus used as the bent axle of the 3rd mode of execution of the present invention of expression.

Fig. 9 is the sectional view of IX-IX line among Fig. 8.

To be expression radially dispose the axial sectional view of wanting portion's formation of the pulley apparatus that the bent axle of multiple row uses with inboard raceways face, outboard raceway face and cylindrical roller to Figure 10.

Figure 11 is the sectional view of XI-XI line among Figure 10.

Figure 12 is the sectional view according to the automatic takeup of the 4th mode of execution of the present invention.

Figure 13 is the side view of automatic takeup.

Figure 14 is the cutaway view Amplified image of D-D line among Figure 12.

Figure 15 is the sectional view (sectional view that comprises axle) of force application device.

Figure 16 is the sectional view of force application device of the A-A line of Figure 15.

Figure 17 is the sectional view of force application device of the B-B line of Figure 15.

Figure 18 is used for illustrating the figure that produces flexible principle at force application device, is the sectional view that near the cylindrical roller of the force application device of the original state shown in Figure 15 amplified.

Figure 19 be expression from original state shown in Figure 180 relative displacement vertically apart from the sectional view of the force application device of the state of x.

Figure 20 is the sectional view of the force application device of variation.

Figure 21 is the sectional view of the force application device of the C-C line among Figure 20.

Embodiment

Below, with reference to accompanying drawing, preferred implementation of the present invention is described.

Fig. 1 is the axial sectional view of wanting portion's formation of the pulley apparatus used as the alternator of first mode of execution of the present invention of expression.The pulley apparatus 1 that alternator is used (the following pulley apparatus 1 that also abbreviates as) is to be installed on the input shaft of the alternator that the subsidiary engine as automobile etc. uses, and volume is hung the device that is used to transmit from the belt of the rotating force of the bent axle of motor.

This pulley apparatus 1 possesses: outer circumferential side cylindraceous that is disposed at this belt pulley hub 2 as the belt pulley hub 2 of inner member, coaxially that forms the approximate circle tubular as the belt pulley member 3 of outer member, rollably be located in cylindrical roller 4 between them as rolling element, be located in two rolling bearings 51,52 between belt pulley hub 2 and the belt pulley member 3 in the axial both sides of this cylindrical roller 4.

Wherein, at the outer circumferential face of belt pulley member 3, be formed with the wavy groove 3a that is used to roll up extension belt 50, this wavy groove is used to transmit the rotating force from the bent axle of motor car engine.In addition, at the inner peripheral surface of this belt pulley member 3, be formed with the outboard raceway face 31 that cylindrical roller 4 rolls.

At the outer circumferential face of belt pulley hub 2, form the inboard raceways face 21 that cylindrical roller 4 rolls with outboard raceway face 31 mutually opposedly.In addition, in interior all sides of this belt pulley hub 2, be inserted with the outstanding input shaft S that is provided with in the never illustrated alternator.Axial central part at the inner peripheral surface of belt pulley hub 2, formed internal thread part 25, the external thread part S1 of the end by will being located at input shaft S combines with internal thread part 25 screw threads, and belt pulley hub 2 can be installed integratedly rotatably with input shaft S.In addition, in the end of interior all sides of belt pulley hub 2, to be used for hexagon wrench that belt pulley hub 2 is combined with input shaft S screw thread in order inserting, and to be formed with the spanner insertion part 26 that inner peripheral surface is made for regular hexagon.

By rolling bearing 51,52 is located between belt pulley hub 2 and the belt pulley member 3, they reciprocally can be rotated relatively, and the radial load of supporting role on belt pulley member 3.

Below, inboard raceways face 21 and the outboard raceway face of being located at respectively on belt pulley hub 2 and the belt pulley member 3 31 described.Fig. 2 is the sectional view of II-II line among Fig. 1.The inboard raceways face 21 of belt pulley hub 2 is to be that 4 different inboard special-shaped roller surface 2k as special-shaped roller surface of the circumferential surface at center constitute by forming with running shaft X with belt pulley hub 2 and belt pulley member 3 continuously.Outboard raceway face 31 is to constitute by the outside abnormity roller surface 3k that forms 4 special-shaped roller surfaces of conduct continuously.

Each the inboard special-shaped roller surface 2k that constitutes inboard raceways face 21 all is identical shaped, and each the special-shaped roller surface 3k in the outside that constitutes outboard raceway face 31 also all is identical shaped.Inboard raceways face 21 (is spent every 90) along the circumferential direction equably is divided into 4 parts, and each partitioning portion is made as inboard special-shaped roller surface 2k respectively.Similarly, outboard raceway face 31 also (is spent every 90) along the circumferential direction equably is divided into 4 parts, and each partitioning portion is set as the special-shaped roller surface 3k in the outside respectively.In addition, between each special- shaped roller surface 2k, 3k, respectively dispose a cylindrical roller 4.

In addition, between belt pulley hub 2 and belt pulley member 3, utilize the inboard special-shaped roller surface 2k and outside abnormity roller surface 3k, form the convergent space portion (wedge-like space portion) that roller surface along the circumferential direction narrows down at interval gradually, and along with the relative rotation between belt pulley hub 2 and the belt pulley member 3, utilize so-called chock effect, the pressure elasticity distortion takes place in cylindrical roller 4.As mentioned above, by inboard raceways face 21 and outboard raceway face 31 are utilized forming continuously of special- shaped roller surface 2k, 3k respectively, inboard raceways face 21 and outboard raceway face 31 are only occupied by special- shaped roller surface 2k, 3k respectively.And each special- shaped roller surface 2k, 3k are along the circumferential direction disposed equably.Like this, the circumferencial direction scope of each special- shaped roller surface 2k, 3k is enlarged respectively to greatest extent, helps to obtain the expansion of the circumferencial direction scope of rotary action power.

Below, the contour shape of outside abnormity roller surface 3k and inboard special-shaped roller surface 2k is described in detail.

The special-shaped roller surface 3k in 4 outsides that constitutes outboard raceway face 31 is respectively concave curved surface.Specifically, the special-shaped roller surface 3k in the outside is, is the circumferential surface at center with the outer ring raceway centre of curvature Co that is positioned at running shaft X than belt pulley hub 2 and belt pulley member 3 (below be also referred to as a center X) more close roller surface (the special-shaped roller surface 3k in this an outside) side.The radius of curvature gro of the special-shaped roller surface 3k in this outside is littler than outboard raceway benchmark radius R o, and this outboard raceway benchmark radius R o is the maximum value of the distance between outboard raceway face 31 and the axle center X and is the radius of a circle circumscribed with the cross section contour of outboard raceway face 31.In addition, in cross sectional view, for 3 special-shaped roller surface 3k in the outside separately, outboard raceway centre of curvature Co be in comprise from the axle center X distance reach peaked outboard raceway maximum diameter position 3m and the axle center X straight line p3 on.

The special-shaped roller surface 2k in 4 inboards that constitutes inboard raceways face 21 is respectively convex surface.Specifically, inboard special-shaped roller surface 2k is, is the circumferential surface at center to be positioned at than axle center X further from the inboard raceways centre of curvature Ci of roller surface (this an inboard abnormity roller surface 2k) side.The radius of curvature gri of this inboard abnormity roller surface 2k is bigger than inboard raceways benchmark radius R i, this inboard raceways benchmark radius R i be inboard raceways face 21 with axle center X between minimum value and value and be radius of a circle with the cross section contour inscribe of inboard raceways face 21.In addition, in cross sectional view, for 3 special-shaped roller surface 2k in inboard separately, inboard raceways centre of curvature Ci be in comprise from the axle center X distance reach minimum value inboard raceways minimum diameter position 2m and the axle center X straight line p2 on.

Have the inboard raceways face 21 of aforesaid shape and the pulley apparatus 1 of outboard raceway face 31 and have rotation urging function (torsion spring function).Below this point is described.

Inboard raceways face 21 and outboard raceway face 31, as mentioned above, because not being is the circumferential surface at center with axle center X, therefore the shape in the space (scroll space) between inboard raceways face 21 and the outboard raceway face 31 can change because of the relative phase between belt pulley hub 2 and the belt pulley member 3 concerns, and the state of the state of Fig. 2 to be the inboard raceways minimum diameter position 2m of the outboard raceway maximum diameter position 3m of outboard raceway face 31 and inboard raceways face 21 be set as same phase.Below this state is called normal condition.Under this normal condition, each cylindrical roller 4 is configured in the circumferential locations of joining with inboard raceways minimum diameter position 2m and outboard raceway maximum diameter position 3m.This normal condition is the outside special-shaped roller surface 3k and inboard special-shaped roller surface 2k to the clamping of cylindrical roller 4 state of (roller surface on the contact position of cylindrical roller 4 at interval) maximum at interval.Like this, under this normal condition, act on compressive force on the cylindrical roller 4 by two roller surface 2k, 3k and can reach minimum value (for example 0).

And, though make the diameter of radial distance between inboard raceways minimum diameter position 2m and the outboard raceway maximum diameter position 3m under the normal condition and cylindrical roller 4 roughly consistent, also can leave some radial clearances (positive gap or negative clearance).

In addition, if begin to make belt pulley hub 2 and the 3 relative rotations of belt pulley member from this normal condition, then cylindrical roller 4 rolls, and the clamping of this cylindrical roller 4 narrows down at interval gradually.Like this along with this relative rotation, the elastic compression distortion is taken place by 31 compressions of inboard raceways face 21 and outboard raceway face in cylindrical roller 4, eliminates the rotary action power (elastic force of rotating the direction of the phase difference that produces because of this is relative to giving between belt pulley hub 2 and the belt pulley member 3; Torsion spring power).

The aspect that produces above-mentioned rotary action power (torsion spring power) is further elaborated.Fig. 3 is the sectional view that is used to illustrate the rotary action power that produces because of belt pulley hub 2 and relative rotation between the belt pulley 3, for easy understanding, only represents the section line of the inboard special-shaped roller surface 2k and outside abnormity roller surface 3k and cylindrical roller 4.Among Fig. 3, expression is fixing with belt pulley hub 2, belt pulley member 3 is rotated counterclockwise angle θ and static state of equilibrium.Under the normal condition, outboard raceway maximum diameter position 3m is positioned at the 3mi place, position on the x axle of Fig. 3, and inboard raceways minimum diameter position 2m also is on the x axle.In addition, under this normal condition, the center P r of cylindrical roller 4 also is on the x axle.When beginning that from this normal condition belt pulley member 3 is rotated counterclockwise angle θ, cylindrical roller 4 can be rolled into position shown in Figure 4 counterclockwise.The revolution angle of the cylindrical roller 4 that is caused by this rolling is angle φ i with respect to inboard raceways centre of curvature Ci.

At this moment, when the center of the contact position between special-shaped roller surface 2k and the cylindrical roller 4 with the inboard is made as Pi, when the center of the contact position between outside abnormity roller surface 3k and the cylindrical roller 4 is made as Po, interval between Pi and the Po can be narrower than inboard raceways minimum diameter position 2m under the normal condition and the interval between the outboard raceway maximum diameter position 3m, and narrower than the diameter 2Rr of cylindrical roller 4 (the radius R r of cylindrical roller 42 times).Like this, cylindrical roller 4 is subjected to vertical force Qi from inboard raceways face 21, and is subjected to vertical force Qo and the pressure elasticity distortion takes place from outboard raceway face 31.Under balance and static state, on cylindrical roller 4, can not act on tangential force basically, as shown in Figure 3, some Ci, Co, Pi, Pr, Po are arranged on the straight line L1.In addition, the vertical force Qo ' that is subjected to from cylindrical roller 4 towards also identical vertical force Qi ' that is subjected to from cylindrical roller 4 towards, belt pulley hub 2 with straight line L1 and belt pulley member 3 of the vector of above-mentioned vertical force Qi and vertical force Qo also identical with straight line L1 towards.In addition, belt pulley member 3 is different with radially (direction of the center P o of the contact position of binding and cylindrical roller 4 and axle center X) of pulley apparatus 1 from the vertical force Qo ' that cylindrical roller 4 is subjected to, thereby not only have this composition radially, also have clockwise composition.Like this, the belt pulley member 3 clockwise moment (below be also referred to as rotation urging moment) of force application component (torsion spring) that can be subjected to rotating.The size of rotation urging moment become ((size of vectorial Qo ') * (axle center X to straight line L1 apart from U1)).

As mentioned above, inboard special-shaped roller surface 2k is a convex surface, and outside abnormity roller surface 3k is a concave curved surface.And inboard special-shaped roller surface 2k and outside abnormity roller surface 3k constitute continuous smoothly curved surface.What do not become continuous smoothly curved surface in inboard raceways face 21 is adjacent inboard special-shaped roller surface 2k position, boundary 21b (with reference to Fig. 2) each other only, and that do not become continuous smoothly curved surface in outboard raceway face 31 only is adjacent outside abnormity roller surface 3k position, boundary 31b (with reference to Fig. 2) each other.Thereby, as long as the contact position between cylindrical roller 4 and the roller surface does not reach these positions, boundary 21b, 31b, then along with little by little (at leisure) variation at interval of the roller surface on counterrotating cylindrical roller 4 contact positions between belt pulley hub 2 and the belt pulley member 3.Like this, by utilizing the illustrated said mechanism of Fig. 3, to the rotary action power of the direction of giving the phase difference that elimination produces because of the relative rotation between belt pulley hub 2 and the belt pulley member 3 between belt pulley hub 2 and the belt pulley member 3.

According to the pulley apparatus 1 that constitutes as described above, can utilize and not use the simple formation of being turned round helical spring etc. to give rotation urging function (torsion spring).That is, utilize this torsion spring, can make the along the circumferential direction flexibly relative rotation of belt pulley member 3 and belt pulley hub 2, can alleviate the change of the rotating speed that causes by bent axle that transmits via belt 50, and transmit rotating force to the input shaft S of alternator.In addition, the shape that can be by changing two special-shaped roller surface 2k, 3k or the external diameter of cylindrical roller 4 etc. make and utilize the characteristic of the torsion spring that above-mentioned formation obtains diversely to change, and the degrees of freedom of its setting becomes high.Thereby, can give suitable elastic force characteristic to the pulley apparatus 1 that this alternator is used according to the specification of alternator or the characteristic of motor etc., can more effectively alleviate from the change of the rotating speed of bent axle transmission.

Therefore in addition,, can alleviate change as described above effectively, compare with the situation of having used pulley apparatus in the past from the rotating speed of bent axle according to the pulley apparatus 1 that this alternator is used, can suppress effectively and belt 50 between the slippage that produces.Thereby, compare with the situation of in the past pulley apparatus, can set the initial tension of belt 50 lower, so just can reduce the load of bent axle, improve the oil consumption performance of motor.

In addition, the pulley apparatus 1 of above-mentioned mode of execution, under the situation that the rolling position between cylindrical roller 4 and inboard raceways face 21 and the outboard raceway face 31 lubricated with oiling agents such as oil or greases, can utilize the rolling viscous resistance of cylindrical roller 4 oiling agent in rolling or stir resistance and give attenuation function, thereby can not only have torsion spring, the external force that also has decay concurrently and acted on and as the attenuation function of the rotary action power of the reaction force of above-mentioned external force.Like this, resonance because of the torsion spring generation etc. can be decayed, be alleviated to the pulley apparatus 1 of present embodiment.

In addition, in this pulley apparatus 1, between belt pulley hub 2 and belt pulley member 3, be folded with rolling bearing 51,52, utilize them to come the radial load of supporting role on belt pulley member 3.Like this, owing to can reduce to act on load load on two special-shaped roller surface 2k, 3k and the cylindrical roller 4, therefore can make for the required load of the active force that rotates stably to act on these two special-shaped roller surface 2k, 3k and the cylindrical roller 4 from the outside.Thereby, can make the rotary action power of utilizing this pulley apparatus 1 to obtain more stable.

In addition, with in the past use turned round helical spring pulley apparatus and compared, can suppress to use continuously or timeliness due to aging, can realize long lifetime.In addition, peripheral structure can be simplified, can realize the minimizingization of part count or assembly cost, the raising of reliability, the miniaturization of this device etc.

Fig. 4 is the sectional view of the pulley apparatus 1 used as the alternator of second mode of execution of the present invention.The main difference point of the present embodiment and first mode of execution is that the mode that is restricted to a direction with the relative sense of rotation that can obtain torsion spring is formed with inboard raceways face 21 and outboard raceway face 31.For other aspect, since identical with first mode of execution, explanation therefore omitted.

The special-shaped roller surface 2k of each of the pulley apparatus 1 of present embodiment, 3k are formed by the curved surface with single radius of curvature respectively, but are formed by the curved surface with two kinds of radius of curvature.That is, inboard special-shaped roller surface 2k is that the inboard rolling surface 2k1 of Gri keeps face 2k2 to constitute with the inboard rolling element with radius of curvature identical with the radius R r of cylindrical roller 4 by radius of curvature respectively.(the path side) end of the side of inboard rolling surface 2k1 becomes inboard raceways minimum diameter position 2m, and this inboard raceways minimum diameter position 2m is set as the boundary between inboard rolling surface 2k1 and the inboard rolling element maintenance face 2k2.In addition, at this 2m place, inboard raceways minimum diameter position, inboard rolling surface 2k1 and inboard rolling element keep face 2k2 continuous smoothly.

In addition, outside abnormity roller surface 3k is that the outside rolling surface 3k1 of Gro keeps face 3k2 to constitute with the outside rolling element with radius of curvature identical with the radius R r of cylindrical roller 4 by radius of curvature respectively.(big footpath side) end of the side of outside rolling surface 3k1 becomes outboard raceway maximum diameter position 3m, and this outboard raceway maximum diameter position 3m is set as the boundary between outside rolling surface 3k1 and the outside rolling element maintenance face 3k2.In addition, at this 3m place, outboard raceway maximum diameter position, outside rolling surface 3k1 and outside rolling element keep face 3k2 continuous smoothly.

State shown in Fig. 4 is that cylindrical roller 4 joins with outboard raceway maximum diameter position 3m and inboard raceways minimum diameter position 2m and keeps face 2k2 and outside rolling element to keep face 3k2 face state of contact with inboard rolling element, and this state is the normal condition in the pulley apparatus 1 of present embodiment.Under this normal condition, act on compressive force on the cylindrical roller 4 from roller surface 21,31 and reach minimum value (for example 0).From this normal condition, belt pulley hub 2 only can be along relative a rotation of direction with belt pulley member 3.That is,, belt pulley member 3 is only begun to being rotated counterclockwise from the normal condition of Fig. 4, and it is turned clockwise if for example consider belt pulley hub 2 is fixing and make the situation of belt pulley member 3 rotations.

Below, the contour shape of outside abnormity roller surface 3k and inboard special-shaped roller surface 2k is described in detail.In special-shaped roller surface 2k, the 3k in the pulley apparatus 1 of present embodiment, different as the The curvature center of the inboard rolling surface 2k1 of cylindrical roller 4 rotatable roller surfaces and outside rolling surface 3k1 with the position shown in first mode of execution.

In the cross section of the normal condition of Fig. 4, will be with to link outboard raceway maximum diameter position 3m parallel with the straight line t1 of inboard raceways minimum diameter position 2m and pass the straight line of center X and be made as the first straight line x1 and the second straight line y1.As shown in Figure 4, the first straight line x1 and the second straight line y1 are mutually orthogonal, utilize these the first straight line x1 and the second straight line y1, the sectional view of Fig. 4 is divided into and waits the zone (the top-right zone from Fig. 4 is followed successively by the regional A3 of regional A1, bottom-right regional A2, left bottom, upper left regional A4 clockwise) of joining several similar numbers (just 4).At this moment, the centre of curvature Ci1 that for example mainly belongs to the inboard rolling surface 2k1 of regional A1 belongs to regional A4.In addition, the centre of curvature Co1 that for example mainly belongs to the outside rolling surface 3k1 of regional A2 belongs to regional A1.That is to say, the centre of curvature of inboard rolling surface 2k1 that mainly belongs to certain zone in 4 zones being divided by above-mentioned straight line x1 and y1 is configured in along in the zone of adjacent other of the belt pulley member sense of rotation that can obtain torsion spring (in this pulley apparatus 1 for counterclockwise).Equally, mainly belong to the centre of curvature of outside rolling surface 3k1 in certain zone in above-mentioned 4 zones, be configured in along in the zone of adjacent other of the belt pulley member sense of rotation that can obtain torsion spring.

Fig. 5 be illustrated in the belt pulley hub 2 of pulley apparatus 1 of present embodiment that is in normal condition fixing after, belt pulley member 3 is rotated counterclockwise angle θ and the figure of static state of equilibrium.Utilize the rotation of this belt pulley member 3, cylindrical roller 4 rolls and with respect to the centre of curvature Ci1 revolution angle φ i of inboard rolling surface 2k1.At this moment, with illustrated in fig. 4 identical, the vertical force Qo ' that belt pulley member 3 is subjected to from cylindrical roller 4, can be identical with the straight line L1 of the centre of curvature Ci1 of center P o that connects the contact position between cylindrical roller 4 and the outer ring raceway face 31 and inboard rolling surface 2k1 towards.Like this, vertical force Qo ' has clockwise composition in Fig. 5, forms the rotation urging moment that produces torsion spring.Here, different with inboard raceways centre of curvature Ci under the situation of Fig. 4, the centre of curvature Ci1 of the inboard rolling surface 2k1 among Fig. 5 (the inboard rolling surface 2k1 that mainly belongs to above-mentioned regional A1), from axle center X along the second straight line y1 direction offsetting distance h.Utilize the offsetting of this distance h, the vector of vertical force Qo ' towards comparing with the situation of Fig. 4, more approach level.In other words, the length of the vertical line of leaving behind to straight line L1 from axle center X becomes the length towards the arm of force of the moment of quadrature with respect to above-mentioned vertical force Qo ', compare with the length U1 of the arm of force of moment under the situation of Fig. 4, the length U2 of the arm of force of the moment under the situation of Fig. 5 is longer.

Thereby, under the big or small identical situation of vertical force Qo ', with rotation urging moment under the situation of Fig. 3 ((vertical force Qo ' size) * (length U1)) compare the rotation urging moment under the situation of Fig. 5 ((vertical force Qo ' size) * (length U2)) bigger.Like this, compare with the situation of Fig. 3, can be under the situation of Fig. 5 at external force (torque) active force that more effectively rotates.That is, can increase rotary action power by the ratio that reduces vertical force Qo ', suitably adjust the balance of rotary action power and attenuation function, active force effectively rotates.

According to the pulley apparatus 1 of the present embodiment that constitutes as described above, owing to can therefore can more effectively alleviate the rotating speed change at the external force active force that rotates effectively.

In addition, the pulley apparatus 1 of present embodiment as mentioned above, is limited to only direction with belt pulley hub 2 with relative rotation between the belt pulley member 3.In addition, regardless of the phase relationship between belt pulley hub 2 and the belt pulley member 3, the rotary action power of the direction of the phase difference that elimination produces because of belt pulley hub 2 and relative rotation between the belt pulley member 3 all only produces along the clockwise direction among Fig. 4, and does not produce in the counterclockwise direction.On the other hand, the alternator of this pulley apparatus 1 is installed, owing to only transmit the rotating force of the bent axle of the motor of rotation in a certain direction, even therefore only along the device of the active force that rotates under the counterrotating situation of direction, also can use.

Below, wait pulley apparatus that being used to of carrying out verify that alternator of the present invention uses that the test result of the mitigation performance of the change of rotating speed is described to inventor.

As the pulley apparatus that is used for this test, prepared the pulley apparatus that the alternator of Figure 1 and Figure 2 is used.It is 0.3 steel as 207900MPa, Poisson's ratio that the belt pulley hub of this pulley apparatus, belt pulley member and cylindrical roller use Young's modulus, and adopts specification shown below to make.

Inner ring raceway benchmark radius R i:13.5mm

Outer ring raceway benchmark radius R o:20mm

Radius of roller Rr (Fig. 2): 3.25mm

Roller effective length: 10mm

Raceway average diameter: 33.5mm

Radial clearance: 0mm

The radius of curvature gri:15.2mm of inner ring abnormity roller surface 2k

The radius of curvature gro:18mm of outer ring abnormity roller surface 3k

Evaluating method as the mitigation performance of the rotating speed of above-mentioned pulley apparatus change has adopted following method.Promptly, have equal quality with alternator and by the axle of free rotary ground supporting on above-mentioned pulley apparatus is installed, on as the belt pulley member of input side, roll up the extension belt, and make the rotation of belt pulley member through the time with changing rotating speed with specified amplitude, frequency.In addition, measure the timeliness of the rotating speed of the axle (belt pulley hub) that rotates along with the rotation of belt pulley member this moment, grasp the amplitude of this rotating speed, carry out the evaluation of the mitigation performance of rotating speed change thus.And the rotating speed of belt pulley member and axle is to measure as the peripheral velocity of same diameter.

As test conditions, will be to have the amplitude of peripheral velocity per minute 320～370m and change as the speed setting of the belt pulley member of input side with some cycles.

Fig. 6 is the plotted curve of the rotating speed of the expression timeliness of having measured the rotating speed of belt pulley member, axle and the result's of timeliness a example.Among the figure, the longitudinal axis is represented rotating speed, and transverse axis is represented the transit time.In addition, waveform H1 represents the timeliness of the rotating speed of belt pulley member, and waveform I1 represents the timeliness of the rotating speed of axle.

If observe waveform H1, then have the amplitude of peripheral velocity per minute 320～370m as can be known and change with some cycles.In addition, if relatively waveform H1 and waveform I1 can be clear that then with respect to the amplitude h of the waveform H of the rotating speed of expression belt pulley member, the amplitude i of the waveform I of the rotating speed of expression axle is very little, the change of the rotating speed that had of belt pulley member is alleviated as can be known.

For as above-mentioned amplitude h that obtains and amplitude i shown in Figure 6ly, with the scope of the frequency setting in the cyclical swing of the rotating speed of belt pulley member, measured amplitude with respect to the rotating speed of the axle of each frequency at 30～70Hz.

Fig. 7 be drawn obtain as described above with respect to the amplitude h of each frequency and the plotted curve of amplitude i.Among the figure, the longitudinal axis is represented the amplitude that rotating speed has, and transverse axis is represented the frequency in the cyclical swing of rotating speed of belt pulley member.Line chart H2 represents the measurement result of belt pulley member, and line chart I2 represents the measurement result of axle.If relatively two line chart H2, I2, then as can be known under each frequency of being measured, with respect to the amplitude of belt pulley member, the amplitude of axle is very little.

According to above test result, can confirm, the pulley apparatus that alternator according to the present invention is used can make the amplitude that changes along with the rotating speed to the transmission of belt pulley member become very little and be delivered to axle (belt pulley hub) under various conditions, can alleviate the rotating speed change effectively.That is, be used for the alternator of motor, can alleviate the rotating speed change of bent axle effectively by this pulley apparatus that will have aforesaid characteristic.

Fig. 8 is the sectional view of wanting portion's formation of the pulley apparatus used as the bent axle of the 3rd mode of execution of the present invention of expression.The pulley apparatus 101 that this bent axle is used is the devices that are installed on the bent axle of motor of automobile, is that volume hangs with the device that is used for the belt that rotating force that bent axle is produced transmits and drive to subsidiary engine classes such as alternators.

The pulley apparatus 101 that this bent axle is used possesses: but one is installed on the inner member 102 on the bent axle CS of motor rotatably; Be disposed at the belt pulley member 103 as outer member cylindraceous of the outer circumferential side of this inner member 102 coaxially; Rollably be located in the cylindrical roller 104 between them as rolling element; Be located in two rolling bearings 151,152 between inner member 102 and the belt pulley member 103 in the axial both sides of this cylindrical roller 104.

Wherein, at the outer circumferential face of belt pulley member 103, be formed with volume and hang the wavy groove 103a be used for the belt 50 that rotating force that the bent axle with motor produces transmits to the subsidiary engine class.In addition, at the inner peripheral surface of this belt pulley member 103, be formed with the outboard raceway face 131 that cylindrical roller 104 rolls.

Inner member 102 possesses: the hub portion 126 that is provided with the through hole 126a that inserts bent axle CS; Annulus 125 with outer circumferential face consistent with the axle center of this through hole 126a; Extend and support a plurality of spoke members 127 of annulus 125 radially from hub portion 126.This inner member 102 is by being inserted in through hole 126a with bent axle CS, and utilizes bolt CS1 to fix, but and is installed on the end of bent axle CS rotatably by one.In addition, at the outer circumferential face of annulus 125, form the inboard raceways face 121 that cylindrical roller 104 rolls with outboard raceway face 131 mutually opposedly.

By rolling bearing 151,152 is located between inner member 102 and the belt pulley member 103, not only can make their rotations relatively reciprocally, but also can the radial load of supporting role on belt pulley member 103.

Below, inboard raceways face 121 and the outboard raceway face of being located at respectively on inner member 102 and the belt pulley member 103 131 described.Fig. 9 is the sectional view of IX-IX line among Fig. 8.The inboard raceways face 121 of annulus 125 (inner member 102) is to be that the different a plurality of inboard special-shaped roller surface 102k as special-shaped roller surface of the circumferential surface at center constitute by forming with running shaft X with inner member 102 and belt pulley member 103 continuously.Outboard raceway face 131 is to constitute by the outside abnormity roller surface 103k that forms the special-shaped roller surface of a plurality of conducts continuously.

Each the inboard special-shaped roller surface 102k that constitutes inboard raceways face 121 all is identical shaped, and each the special-shaped roller surface 103k in the outside that constitutes outboard raceway face 131 also all is identical shaped.Inboard raceways face 121 is divided into 8 parts by (each 45 degree) equably in a circumferential direction, and each partitioning portion is set as inboard special-shaped roller surface 102k respectively.Similarly, outboard raceway face 131 also is divided into 8 parts by (each 45 degree) equably in a circumferential direction, and each partitioning portion is set as the special-shaped roller surface 103k in the outside respectively.In addition, between each special-shaped roller surface 102k, 103k, respectively dispose 1 cylindrical roller 104.

In addition, between inner member 102 and belt pulley member 103, utilize the inboard special-shaped roller surface 102k and outside abnormity roller surface 103k, form the convergent space portion (wedge-like space portion) that roller surface narrows down at interval in a circumferential direction gradually, along with the relative rotation between inner member 102 and the belt pulley member 103, utilize so-called chock effect, the pressure elasticity distortion takes place in cylindrical roller 104.As mentioned above, by inboard raceways face 121 and outboard raceway face 131 are utilized forming continuously of special-shaped roller surface 102k, 103k respectively, inboard raceways face 121 and outboard raceway face 131 are only occupied by special-shaped roller surface 102k, 103k respectively.And each special-shaped roller surface 102k, 103k are along the circumferential direction disposed equably.

Below, the contour shape of outside abnormity roller surface 103k and inboard special-shaped roller surface 102k is described in detail.

The a plurality of outside abnormity roller surface 103k that constitute outboard raceway face 131 are set as concave curved surface respectively.Specifically, the special-shaped roller surface 103k in the outside is set as, and is the circumferential surface at center with the outer ring raceway centre of curvature Co that is positioned at running shaft X than inner member 102 and belt pulley member 103 (below be also referred to as a center X) more close roller surface (the special-shaped roller surface 103k in this an outside) side.The radius of curvature gro of the special-shaped roller surface 103k in this outside is littler than outboard raceway benchmark radius R o, and this outboard raceway benchmark radius R o is the maximum value of the distance between outboard raceway face 131 and the axle center X and is the radius of a circle circumscribed with the cross section contour of outboard raceway face 131.In addition, in cross sectional view, for 3 special-shaped roller surface 103k in the outside separately, outboard raceway centre of curvature Co be in comprise from the axle center X distance reach peaked outboard raceway maximum diameter position 103m and the axle center X straight line p103 on.

The special-shaped roller surface 102k in a plurality of inboards that constitutes inboard raceways face 121 is set as convex surface respectively.Specifically, to be set as to be positioned at than axle center X be the circumferential surface at center further from the inboard raceways centre of curvature Ci of roller surface (this an inboard abnormity roller surface 102k) side to inboard special-shaped roller surface 102k.The radius of curvature gri of this inboard abnormity roller surface 102k is bigger than inboard raceways benchmark radius R i, this inboard raceways benchmark radius R i be inboard raceways face 121 with axle center X between minimum value and value and be radius of a circle with the cross section contour inscribe of inboard raceways face 121.In addition, in cross sectional view, for 3 each inboard special-shaped roller surface 102k separately, inboard raceways centre of curvature Ci be in comprise from the axle center X distance reach minimum value inboard raceways minimum diameter position 102m and the axle center X straight line p102 on.

Have the pulley apparatus 101 that the bent axle of the inboard raceways face 121 of aforesaid shape and outboard raceway face 131 uses and have rotation urging function (torsion spring function).To describe this point below.

Inboard raceways face 121 and outboard raceway face 131 are as mentioned above, because not being is the circumferential surface at center with axle center X, therefore the shape in the space (scroll space) between inboard raceways face 121 and the outboard raceway face 131 can change because of the relative phase between inner member 102 and the belt pulley member 103 concerns, and the state of the state of Fig. 9 to be the inboard raceways minimum diameter position 102m of the outboard raceway maximum diameter position 103m of outboard raceway face 131 and inboard raceways face 121 be set as same phase.Below this state is called normal condition.Under this normal condition, each cylindrical roller 104 is configured in the circumferential locations of joining with inboard raceways minimum diameter position 102m and outboard raceway maximum diameter position 103m.This normal condition is the outside special-shaped roller surface 103k and inboard special-shaped roller surface 102k to the clamping of cylindrical roller 104 state of (roller surface on the contact position of cylindrical roller 104 at interval) maximum at interval.Like this, under this normal condition, act on compressive force on the cylindrical roller 104 by two roller surface 102k, 103k and reach minimum value (for example 0).

And, though make inboard raceways minimum diameter position 102m under the normal condition and the radial distance between the outboard raceway maximum diameter 103m, roughly consistent with the diameter of cylindrical roller 104, also can leave some radial clearances (positive gap or negative clearance).

In addition, if begin to make inner member 102 and the 103 relative rotations of belt pulley member from this normal condition, then cylindrical roller 104 rolls, and the clamping of this cylindrical roller 104 narrows down at interval gradually.Like this along with this relative rotation, the elastic compression distortion is taken place by 131 compressions of inboard raceways face 121 and outboard raceway face in cylindrical roller 104, gives between member 102 and the belt pulley member 103 to the inside and eliminates the rotary action power (elastic force of rotating the direction of the phase difference that produces because of this is relative; Torsion spring power).

And, the relation of above-mentioned inboard raceways face 121, outboard raceway face 131 and cylindrical roller 104, identical with the relation of inboard raceways face 21, outboard raceway face 31 and cylindrical roller 4 in first mode of execution, the generation mechanism of the rotary action power between inner member 102 and the belt pulley member 103 is identical with the explanation of the Fig. 3 in above-mentioned first mode of execution, so detailed.

The pulley apparatus of using according to the bent axle that constitutes as described above 101 can be given rotation urging function (torsion spring) by not using the simple formation of being turned round helical spring etc.Promptly, utilize this torsion spring, can make the along the circumferential direction flexibly relative rotation of belt pulley member 103 and inner member 102, belt pulley member 103 is played a role as the vibration damping material at bent axle and alleviate the vibration of bent axle, and alleviate the rotating speed change of bent axle.

In addition, the shape by changing two special-shaped roller surface 102k, 103k or external diameter of cylindrical roller 104 etc. can make and utilize the characteristic of the torsion spring that above-mentioned formation obtains diversely to change, and the degrees of freedom of its setting becomes high.Thereby, can give suitable elastic force characteristic to the pulley apparatus 101 that this bent axle is used according to the specification of motor or characteristic etc., can more effectively alleviate the vibration or the rotating speed change of bent axle.

In addition, the pulley apparatus of using according to this bent axle 101, can alleviate the change of the vibration of bent axle or rotating speed as described above effectively, therefore compare with the situation of the pulley apparatus that has used bent axle in the past to use, can suppress effectively and belt 50 between the slippage that produces.Thereby the situation of the pulley apparatus of using with bent axle is in the past compared, and can set the initial tension of belt 50 lower.Can reduce the load of bent axle like this, improve the oil consumption performance of motor.

In addition, in the pulley apparatus 101 that the bent axle of above-mentioned mode of execution is used, under the situation that the rolling position between cylindrical roller 104 and inboard raceways face 121 and the outboard raceway face 131 lubricated with oiling agents such as oil or greases, can utilize the rolling viscous resistance of the oiling agent of cylindrical roller 104 in rolling or stir resistance and give attenuation function, thereby can have torsion spring, the external force that also has decay concurrently and acted on and as the attenuation function of the rotary action power of the reaction force of above-mentioned external force.Like this, resonance that produces because of torsion spring etc. can be decayed, be alleviated to the pulley apparatus 101 used of the bent axle of present embodiment.

In addition, in the pulley apparatus 101 that this bent axle is used, between inner member 102 and belt pulley member 103, be folded with rolling bearing 151,152, utilize them to come the radial load of supporting role on belt pulley member 103.Like this, owing to can reduce to act on the load load on two special-shaped roller surface 102k, 103k and the cylindrical roller 104, therefore the load required in order to rotate active force stably acted on these two special-shaped roller surface 102k, 103k and the cylindrical roller 104 from the outside.Thereby the rotary action power that the pulley apparatus 101 that utilizes this bent axle to use is obtained is more stable.

In addition, the pulley apparatus of using according to the bent axle of present embodiment 101, with in the past use the pulley apparatus of the vibration isolation rubber made by elastomer etc. compare, can suppress to use continuously or timeliness due to aging, can realize the raising of long lifetime, reliability.

In addition, as Figure 10, shown in Figure 11, also can be formed with inboard special-shaped roller surface 102k inboard raceways face 121, be formed with the outside special-shaped roller surface 103k outboard raceway face 131 and cylindrical roller 104 radially dispose multiple row.Under this situation,, and can increase and allow angle of rotation, therefore can further improve the remission effect of the vibration or the rotating speed change of bent axle because torsional rigid reduces.

Figure 12 and Figure 13 are respectively according to the sectional view of the automatic takeup of the 4th mode of execution of the present invention and side view.Among Figure 12, swing arm 230 is to extend with the base end part 203 of approximate tubular with from this base end part 203 and be fixed with the integrally formed formed parts of arm 207 that volume is hung the belt pulley 206 of belt 50.Belt pulley 206 heart portion therein is equipped with ball bearing 208.The inner ring of this ball bearing 208 is embedded in the front end 207a of arm 207 outward, and is fixed in front end 207a by bolt 209 and nut 210.As, belt pulley 206 is fixed on the front end 207a of arm 207 with rotating freely.

On the other hand, the support member 202 of supporting swing arm 230 is the formed parts that have the axial region 225 that forms the hollow shaft shape and be used for fixing the fixing part 226 on the motor that this automatic takeup 201 is installed.Axial region 225 is disposed at interior all sides of base end part 203 coaxially, between this axial region 225 and base end part 203, rollably is folded with the cylindrical roller 204 as rolling element.In addition,, be formed with the outboard raceway face 231 that cylindrical roller 204 rolls, and on the outer circumferential face of axial region 225, form the inboard raceways face 221 that cylindrical roller 204 rolls mutually opposedly with outboard raceway face 231 at the inner peripheral surface of base end part 203.

Between base end part 203 and axial region 225, be folded with rolling bearing 251,252 in the mode of the axial both sides that are positioned at cylindrical roller 204, thereby can make the reciprocally relative rotation of base end part 203 and axial region 225, and the radial load of supporting role on base end part 203.In addition, on the end of axial region 225, be pressed into the chimeric pushing member 253 that has, this pushing member is used for fixing cylindrical roller 204 and rolling bearing 251,252 to prevent to deviate from from axial region 225.

Below, inboard raceways face 221 and the outboard raceway face of being located at respectively on axial region 225 and the base end part 203 231 described.Figure 14 is the cutaway view Amplified image of D-D line among Figure 12.The inboard raceways face 221 of axial region 225 is to be that 4 different inboard special-shaped roller surface 202k as special-shaped roller surface of the circumferential surface at center constitute by forming with running shaft X with axial region 225 and base end part 203 continuously.Outboard raceway face 231 is to constitute by the outside abnormity roller surface 203k that forms 4 special-shaped roller surfaces of conduct continuously.

Each the inboard special-shaped roller surface 202k that constitutes inboard raceways face 221 all is identical shaped, and each the special-shaped roller surface 203k in the outside that constitutes outboard raceway face 231 also all is identical shaped.Inboard raceways face 221 (is spent every 90) along the circumferential direction equably is divided into 4 parts, and each partitioning portion is made as inboard special-shaped roller surface 202k respectively.Similarly, outboard raceway face 231 also (is spent every 90) along the circumferential direction equably is divided into 4 parts, and each partitioning portion is made as the special-shaped roller surface 203k in the outside respectively.In addition, between each special-shaped roller surface 202k, 203k, respectively dispose a cylindrical roller 204.

In addition, between axial region 225 and base end part 203, utilize the inboard special-shaped roller surface 202k and outside abnormity roller surface 203k, form the convergent space portion (wedge-like space portion) that roller surface along the circumferential direction narrows down at interval gradually, relative rotation along with axial region 225 and base end part 203, utilize so-called chock effect, the pressure elasticity distortion takes place in cylindrical roller 204.As mentioned above, by inboard raceways face 221 and outboard raceway face 231 are utilized forming continuously of special-shaped roller surface 202k, 203k respectively, inboard raceways face 221 and outboard raceway face 231 are only occupied by special-shaped roller surface 202k, 203k respectively.And each special-shaped roller surface 202k, 203k are along the circumferential direction disposed equably.

Below, the contour shape of outside abnormity roller surface 203k and inboard special-shaped roller surface 202k is described in detail.

The special-shaped roller surface 203k in 4 outsides that constitutes outboard raceway face 231 is set as concave curved surface respectively.Specifically, to be set as the outer ring raceway centre of curvature Co to be positioned at running shaft X than axial region 225 and base end part 203 (below be also referred to as a center X) more close roller surface (the special-shaped roller surface 203k in this an outside) side be the circumferential surface at center to outside abnormity roller surface 203k.The radius of curvature gro of the special-shaped roller surface 203k in this outside is littler than outboard raceway benchmark radius R o, and this outboard raceway benchmark radius R o is the maximum value of the distance between outboard raceway face 231 and the axle center X and is the radius of a circle circumscribed with the cross section contour of outboard raceway face 231.In addition, in cross sectional view, for 3 each the outside special-shaped roller surface 203k separately, outboard raceway centre of curvature Co be in comprise from the axle center X distance reach peaked outboard raceway maximum diameter position 203m and the axle center X straight line p203 on.

The special-shaped roller surface 202k in 4 inboards that constitutes inboard raceways face 221 is set as convex surface respectively.Specifically, to be set as to be positioned at than axle center X be the circumferential surface at center further from the inboard raceways centre of curvature Ci of roller surface (this an inboard abnormity roller surface 202k) side to inboard special-shaped roller surface 202k.The radius of curvature gri of this inboard abnormity roller surface 202k is bigger than inboard raceways benchmark radius R i, this inboard raceways benchmark radius R i be inboard raceways face 221 with axle center X between minimum value and value and be radius of a circle with the cross section contour inscribe of inboard raceways face 221.In addition, in cross sectional view, for 3 each inboard special-shaped roller surface 202k separately, inboard raceways centre of curvature Ci be in comprise the distance of center X reach minimum value inboard raceways minimum diameter position 202m and the axle center X straight line p202 on.

Be provided with the bent axle 225 and the base end part 203 of two roller surfaces 221,231 of aforesaid shape, when they rotate relatively, have the rotation urging function (torsion spring function) of rotating the direction of the phase difference that produces relatively along with this towards eliminating.To describe this point below.

Inboard raceways face 221 and outboard raceway face 231 are as mentioned above, because not being is the circumferential surface at center with axle center X, therefore the shape in the space (scroll space) between inboard raceways face 221 and the outboard raceway face 231 can change because of the relative phase between axial region 225 and the base end part 203 concerns, and the state of the state of Figure 14 to be the inboard raceways minimum diameter position 202m of the outboard raceway maximum diameter position 203m of outboard raceway face 231 and inboard raceways face 221 be set as same phase.Below this state is called normal condition.Under this normal condition, each cylindrical roller 204 is configured in the circumferential locations of joining with inboard raceways minimum diameter position 202m and outboard raceway maximum diameter position 203m.This normal condition is the outside special-shaped roller surface 203k and inboard special-shaped roller surface 202k to the clamping of cylindrical roller 204 state of (roller surface on the contact position of cylindrical roller 204 at interval) maximum at interval.Like this, under this normal condition, act on compressive force on the cylindrical roller 204 by two roller surface 202k, 203k and reach minimum value (for example 0).

And, though make the diameter of radial distance between inboard raceways minimum diameter position 202m and the outboard raceway maximum diameter 203m under the normal condition and cylindrical roller 204 roughly consistent, also can leave some radial clearances (positive gap or negative clearance).

In addition, if begin to make axial region 225 and base end part 203 relative rotations from this normal condition, then cylindrical roller 204 rolls, and the clamping of this cylindrical roller 204 narrows down at interval gradually.Like this along with this relative rotation, the elastic compression distortion is taken place by 231 compressions of inboard raceways face 221 and outboard raceway face in cylindrical roller 204, eliminates the rotary action power (elastic force of rotating the direction of the phase difference that produces because of this is relative to giving between axial region 225 and the base end part 203; Torsion spring power).

And, the relation of inboard raceways face 21, outboard raceway face 31 and cylindrical roller 4 in the relation of above-mentioned inboard raceways face 221, outboard raceway face 231 and cylindrical roller 204 and first mode of execution is identical, the generation mechanism of the rotary action power between inner member 202 and the base end part 203 is identical with the explanation of the Fig. 3 in above-mentioned first mode of execution, so detailed.

As mentioned above, axial region 225 can support base end part 203 with the relative rotation, and swing arm 230 can be with respect to support member 202 swings.Automatic takeup 201 hangs with under the state of belt 50 at volume on the belt pulley 206 swing arm 230 is utilized the clockwise direction application of force of above-mentioned rotary action power along Figure 13, gives certain force of strain to belt 50.

According to the automatic takeup 201 that constitutes as described above, can come giving rotation urging function (torsion spring) between axial region 225 (axle support member 202) and the base end part 203 by not using the simple formation of being turned round helical spring etc.That is, utilize this torsion spring, can make swing arm 230 is the central elastic swing with axial region 225, can give tension force to belt 50.In addition, the shape by changing two special-shaped roller surface 202k, 203k or the external diameter of cylindrical roller 204 etc. can make and utilize the characteristic of the torsion spring that above-mentioned formation obtains diversely to change, and the degrees of freedom of its setting becomes high.Thereby, can be according to the specification of motor or characteristic etc., set the elastic force characteristic in swing arm 230 swings rightly, can more effectively absorb the tension change of belt 50.

In addition, in the automatic takeup 201 of above-mentioned mode of execution, under the situation that the rolling position between cylindrical roller 204 and inboard raceways face 221 and the outboard raceway face 231 lubricated with oiling agents such as oil or greases, can utilize the rolling viscous resistance of the oiling agent of cylindrical roller 204 in rolling or stir resistance and give attenuation function, thereby can have torsion spring, the external force that also has decay concurrently and acted on and as the attenuation function of the rotary action power of the reaction force of above-mentioned external force.Like this, resonance that produces because of torsion spring etc. can be decayed, be alleviated to the automatic takeup 201 of present embodiment.

In addition, in this automatic takeup 201, between axial region 225 and base end part 203, be folded with rolling bearing 251,252, utilize them to come the radial load of supporting role between axial region 225 and base end part 203.Like this, owing to can reduce to act on the load load on two special-shaped roller surface 202k, 203k and the cylindrical roller 204, therefore the load required in order to rotate active force stably acted on these two special-shaped roller surface 202k, 203k and the cylindrical roller 204 from the outside.Thereby, can make the rotary action power of utilizing this automatic takeup 201 to obtain more stable.

In addition, with in the past use turned round helical spring automatic takeup and compared, can suppress to use continuously or timeliness due to aging, can realize long lifetime.In addition, peripheral structure can be simplified, the minimizingization of part count or assembly cost, the raising of reliability, the miniaturization of this automatic takeup etc. can be realized.

And pulley apparatus of the present invention and automatic takeup are not limited to the respective embodiments described above.For example, in the pulley apparatus and automatic takeup that the pulley apparatus that alternator is in the respective embodiments described above used, bent axle are used, though used cylindrical roller as rolling element, yet for example also can use ball or tapered roller etc., so long as the rolling element that rolls along with the relative rotation of two roller surfaces, then be not particularly limited for shape of rolling element etc.In addition, in order to improve the setting degrees of freedom of torsional rigid, also can use the hollow rolling element (for example hollow cylindrical roller or hollow ball) of easy elastic compression distortion etc.In addition, the material of rolling element can suitably be selected accordingly with the desired performance of each pulley apparatus.

In addition, in the pulley apparatus that pulley apparatus that the alternator of above-mentioned mode of execution is used and bent axle are used, though the inner peripheral surface at belt pulley member cylindraceous directly is formed with the outboard raceway face, however for example also can be by on the inner peripheral surface that will be entrenched in the belt pulley member and the outboard raceway face is set in the inner peripheral surface side of this belt pulley member in the outer ring that inner peripheral surface is formed with the outboard raceway face.In addition, in the base end part or axial region of the tubular in the automatic takeup of inner member (belt pulley hub), above-mentioned mode of execution, also can roller surface be set similarly by chimeric interior (outward) circle that is formed with each roller surface.

In addition, belt pulley member in the pulley apparatus that bent axle of the present invention is used, can be by adjusting its shape or wall thickness, suitably adjust overall weight, and, further improve remission effect to the vibration or the rotating speed change of bent axle by improving the effect in this pulley apparatus as the vibration damping object.

In addition, in the automatic takeup shown in above-mentioned the 4th mode of execution, though in swing arm 230, illustration the example that base end part 203 and arm 207 are shaped integratedly, but for example also base end part 203 and arm 207 can be shaped as independent component, constitute swing arm by they are fixed as one.

Below, the relevant invention that has the force application device of spring on straight moving direction (compression direction or draw direction) is described.

As the force application device of on compression direction or draw direction, giving spring, use helical spring (compression helical spring or draft helical spring etc.) or resilient member (rubber etc.) etc. widely.For example used helical spring force application device to produce resiliently deformable, the outside has been given the active force of the direction of eliminating this displacement with respect to the displacement vertically of this helical spring.This kind force application device need to be used to the various uses of spring, for example be loaded in the spring-elastic described in the flat 7-224850 communique of TOHKEMY be coupling first-class in and utilize.

But having used in the past the force application device of helical spring etc. has variety of issue.

The first, force application component in the past wears out because of use or timeliness continuously easily, and the problem that the life-span lacks is arranged.

The second, in the above-mentioned force application device in the past, the low problem of design freedom is arranged.For example in order to change the spring rigidity, for helical spring situation, change the number of turns or roll diameter etc., for the situation of having used resilient members such as rubber, changing the material or the thickness of resilient member, is limited yet utilize the scope of design of the spring rigidity that these changes obtain.Thereby, in the force application component in the past, utilize identical size (bodily form) the scope of getable spring rigidity very limited.In addition, in the force application component in the past, the relation between displacement and the spring constant is linear, can't spring constant and displacement freely be changed accordingly as making spring constant changes etc. with respect to non-linear displacement ground.

The 3rd, because the joining portion that in the past force application device needs force application components such as first member that will reciprocally relatively move and second member and helical spring to engage, it is complicated that peripheral structure becomes, and therefore the problem that part count or assembly cost increase and reliability reduces is arranged.

The 4th, in the force application device in the past, because as mentioned above, design freedom is low, and peripheral structure becomes complicated easily, so the size of force application device (bodily form) becomes big easily, and is restricted aspect miniaturization.

As mentioned above, used the force application device of helical spring etc. that variety of issue arranged.With respect to this, the present invention is based on the member of the new structure of finishing with diverse technological thought in the past, is the force application device that can solve above-mentioned each problem.

That is, the objective of the invention is to the epoch-making force application device of the variety of issues that force application component had in the past such as helical spring that have been resolved.

The invention provides a kind of force application device, it is characterized in that, possess: first member with first roller surface, have and opposed second roller surface of above-mentioned first roller surface and can and above-mentioned first member between second member that moves of straight line relatively, rollably be located in the rolling element between above-mentioned first roller surface and second roller surface, at least one side of above-mentioned first roller surface and second roller surface has special-shaped roller surface at least a portion, this abnormity roller surface is on one side along with above-mentioned first member rolls rolling element with moving relative to straight line of second member, the clamping that reduces on one side this rolling element is gradually moved the active force of the direction of relative displacement these members of producing between because of above-mentioned relative to straight line to giving elimination between above-mentioned first member and second member at interval.

According to this formation, can not use ground such as helical spring to give application of force function (below be also referred to as springiness).In addition, can utilize rolling element to come the load of supporting role between first member and second member.In addition, can utilize the design of special-shaped roller surface freely to design spring rigidity etc., it is high that design freedom becomes.

In above-mentioned force application device, also can adopt following formation, that is, above-mentioned special-shaped roller surface is formed in the curved surface that above-mentioned cross section on the movement direction that straight line moves becomes sag vertical curve.Under this situation, if so be provided with, then move relative to straight line along with above-mentioned, rolling element is easy to roll more smoothly contact and moves.In addition, be easy to reduce along with moving the rolling element clamping variance ratio at interval that narrows down gradually relative to straight line between above-mentioned first member and second member.In wideer relative displacement scope, guarantee springiness like this, easily.

In this force application device, also can adopt following formation, that is, have: above-mentioned first member, it has the lateral part of tubulose, and the inner face of this lateral part is set as above-mentioned first roller surface; Above-mentioned second member, it has coaxial and be disposed at the inside portion of the inside of this lateral part with above-mentioned lateral part, and the outside of this inside portion is set as above-mentioned second roller surface; The above-mentioned special-shaped roller surface that at least one face of the outside of the inner face of above-mentioned lateral part and above-mentioned inside portion, is provided with, above-mentioned first roller surface, second roller surface and above-mentioned rolling element are disposed equably around axle, above-mentioned lateral part and above-mentioned inside portion can be moved relative to straight line when keeping coaxial state vertically.

If so be provided with, then because in the lateral part of tubulose, and be disposed between its inboard inside portion and dispose rolling element, therefore by special-shaped roller surface being set, be easy to obtain to utilize axial between first member and second member to move the formation that the clamping interval with rolling element narrows down gradually relative to straight line at the inner face of lateral part or the outside of inside portion.In addition, because roller surface and rolling element are disposed equably around axle, the power perpendicular to the direction of axle that therefore acts on along with the compression of rolling element in the power on each member is cancelled.Like this, be easy to obtain along with moving the formation that produces axial active force relative to straight line between first member and second member.

As mentioned above, according to force application device of the present invention, by utilize special-shaped roller surface to can between the member that straight line moves, give springiness such with diverse technological thought in the past, can form force application device with excellent characteristic.

Below, in the reference accompanying drawing, the mode of execution of the force application device that the present invention relates to is described.

Figure 15 is the sectional view (long side direction sectional view) of force application device 301, and Figure 16 is the sectional view of the A-A line of Figure 15, and Figure 17 is the sectional view of the B-B line of Figure 15.

Force application device 301 possesses: first member 303 with first roller surface 303f; Have with the opposed second roller surface 305f of the first roller surface 303f and can and first member 303 between move second member 305 of (moving) relative to straight line relative to parallel; Rollably be located in the cylindrical roller 306 between the first roller surface 303f and the second roller surface 305f as rolling element.

The outside of first member 303 is rectangular-shaped for being similar to, and has hollow part t in inside, and in its long side direction one distolateral open shape of hollow part t and external communications ground that is formed.That is to say that first member 303 has sectional shape and is the lateral part 303a of the tubulose of approximate dimetric ring-type, the bottom 303b that the long side direction the other end side seal of this lateral part 303a is stifled.

On the other hand, second member 305 has from the inside portion 305a of the inside of the distolateral lateral part 303a that is inserted in first member 303 of the opening of this first member 303.In addition, between the inside portion 305a of the lateral part 303a of first member 303 and second member 305, rollably be folded with cylindrical roller 306.

First member 303 and second member 305 can (long side direction of inside portion 305a and lateral part 303a) is reciprocally relative vertically as piston motion move back and forth.When making first member 303 and second member 305 when straight line moves, be located in first member 303 and roll to contact with each cylindrical roller 306 between second member 305 and move.

But as shown in figure 15, the cross section of the first roller surface 303f on the relative straight line movement direction (i.e. axle z direction) of first member 303 and second member 305 of being located on first member 303 is made into not relative with this straight line movement direction parallel in shape.Specifically, the first roller surface 303f has special-shaped roller surface 303k, and this abnormity roller surface is formed in the curved surface that above-mentioned cross section (being the axial cross section of Figure 15) on the movement direction that straight line moves becomes sag vertical curve.

Similarly, the cross section of the second roller surface 305f on above-mentioned relative straight line movement direction (promptly axial) of being located on second member 305 is made into not relative with this straight line movement direction parallel in shape.Specifically, the second roller surface 305f has special-shaped roller surface 305k, and this abnormity roller surface is formed in the curved surface that above-mentioned cross section (being the axial cross section of Figure 15) on the movement direction that straight line moves becomes sag vertical curve.Thereby, along with moving relative to straight line between first member 303 and second member 305, the clamping that is located in the cylindrical roller 306 between these special-shaped roller surface 303k and the special-shaped roller surface 305k changes according to the relative position relation between first member 303 and second member 305 at interval.

Though the special-shaped roller surface 303k of the first roller surface 303f has the curvature of regulation in axial cross section, yet this curvature is set necessarily.On the other hand, special-shaped roller surface 303k be with axially vertical cross section (Figure 16) in do not have curvature face.That is to say that special-shaped roller surface 303k is set as circumferential surface.This point also is identical with special-shaped roller surface 305k.That is, the special-shaped roller surface 305k of the second roller surface 305f has the curvature of regulation in axial cross section, and this curvature is set as necessarily, and special-shaped roller surface 305k be with axially vertical cross section (Figure 16) in do not have curvature circumferential surface.By special-shaped roller surface 303k, 305k are made as circumferential surface, compare the design of special-shaped roller surface and to add trade union more easy with situations such as free form surfaces.

Among the first roller surface 303f, special-shaped roller surface 303k is provided with continuously along axle z direction.That is, special-shaped roller surface 303k is provided with continuously with axial one distolateral (opening side of first member 303) and axial another distolateral (bottom 303b side of first member 303).Like this, can guarantee the axial range of each special-shaped roller surface 303k to greatest extent, help to obtain the expansion of the relative shifting range of active force.

Similarly, in the second roller surface 305f, special-shaped roller surface 305k is provided with continuously along axle z direction.That is, special-shaped roller surface 305k is provided with continuously with axial one distolateral (opening side of first member 303) and axial another distolateral (bottom 303b side of first member 303).Like this, can guarantee the axial range of each special-shaped roller surface 305k to greatest extent, help to obtain the expansion of the relative shifting range of active force.

303k is identical with the curvature that special-shaped roller surface 305k is set as on axial cross section for the abnormity roller surface.In addition, in original state shown in Figure 15, the axial range of special-shaped roller surface 303k is with identical with the axial range of the opposed special-shaped roller surface 305k of this abnormity roller surface 303k.This point also helps to obtain the expansion of the relative shifting range of active force.And so-called original state is meant the state that does not act on active force between first member 303 and second member 305.In addition, in the axial cross section of Figure 15, the tangent line (not shown) that the deep-seated of special-shaped roller surface 303k is put the 303m place is set as parallel with axle z.Similarly, the deep-seated of the special-shaped roller surface 305k tangent line of putting the 305m place is set as parallel with axle z.In the sectional view of the original state of Figure 15, the centre of curvature (not shown) of special-shaped roller surface 303k and special-shaped roller surface 305k is in the deep-seated that the deep-seated that links on the special-shaped roller surface 303k puts on 303m and the special-shaped roller surface 305k and puts on the straight line s (with reference to Figure 15) of 305m.

As can be known, the force application device 301 of present embodiment has each 8 of special-shaped roller surface 303k and special-shaped roller surface 305k from Figure 15 and Figure 16.

That is, as shown in figure 16, special-shaped roller surface 303k is located at the cross section respectively and is on 4 inner faces that are similar to foursquare lateral part 303a.That is to say that special-shaped roller surface 303k is disposed equably around axle z.Similarly, special-shaped roller surface 305k is located at respectively on 4 outsides that the cross section is approximate foursquare inside portion 305a.That is to say that special-shaped roller surface 305k is disposed equably around axle z.In addition, as mentioned above, since special-shaped roller surface 303k, special-shaped roller surface 305k respectively by with axial one distolateral and another distolaterally be provided with continuously, therefore special-shaped roller surface 303k and special-shaped roller surface 305k add up to respectively and respectively are provided with 8, under above-mentioned original state, form the group of 8 groups of abnormity roller surface 303k and special-shaped roller surface 305k.In addition, dispose 1 rolling element (cylindrical roller 306) with respect to one group of abnormity roller surface 303k and special-shaped roller surface 305k.Like this, force application device 301 totals have 8 cylindrical rollers 306.Thereby, dispose equably around axle (every 90 degree) respectively: be disposed at axial one distolateral and first line column roller 361 that constitute by 4 cylindrical rollers 306; Be disposed at axially another secondary series cylindrical roller 362 distolateral and that constitute by 4 cylindrical rollers 306.

In the force application device 301 of aforesaid formation, abnormity roller surface 303k and special-shaped roller surface 305k are on one side along with moving and make cylindrical roller 306 rollings relative to straight line between the first roller surface 303f and the second roller surface 305f, the clamping that reduces on one side this cylindrical roller 306 gradually and is moved the active force of the direction of the first roller surface 303f that produce and relative displacement second roller surface 305f between because of above-mentioned relative to straight line to giving elimination between first member 303 and second member 305 at interval.Below, this point is elaborated.

Figure 18 is in the force application device 301 of original state shown in Figure 15, the sectional view that a near cylindrical roller 306 amplified.Under this original state, the deep-seated on the special-shaped roller surface 303k is put 303m and is set as identical with the axial position that the deep-seated on the special-shaped roller surface 305k is put 305m.Like this, cylindrical roller 306 becomes and puts 303m with deep-seated and deep-seated is put the state that 305m joins.As mentioned above, along with moving relative to straight line of first member 303 and second member 305, the clamping of cylindrical roller 306 changes at interval, and this clamping is issued to maximum in above-mentioned original state at interval.Like this under original state, that the compressive stress that acts on cylindrical roller 306 by special-shaped roller surface 303k, 305k reaches is minimum (for example 0).And, under this original state, deep-seated on the abnormity roller surface 303k is put the distance that the deep-seated on 303m and the special-shaped roller surface 305k puts between the 305m and is set as with the diameter of cylindrical roller 306 roughly the same, gap between each roller surface 303k, 305k and the cylindrical roller 306 is roughly zero, yet for example also can be provided with-gap (positive gap, negative clearance) about 0.03mm～0.03mm.

When begin to make first member 303 and second member 305 when straight line moves from original state, along with this moves relative to straight line, cylindrical roller 306 moves when rolling.Because this rolls, the contact position of cylindrical roller 306 and two roller surface 303k, 305k leaves deep-seated and puts 303m, 305m, and the clamping interval of cylindrical roller 306 is compared also with original state and narrowed down gradually.

Here, for under the state that first member 303 is fixed, second member 305 being applied axial external force, formation begins member 303,305 vertically with the state of distance x relative displacement from original state shown in Figure 180, describes because of the force balance of above-mentioned external force and force application device 301 is in static state (being shown among Figure 19).Under the state of above-mentioned Figure 19 with distance x relative displacement, it is narrower than the diameter of cylindrical roller 306 that the clamping of cylindrical roller 306 becomes at interval.Like this, cylindrical roller 306 is subjected to vertical force F1, F2 and the elastic compression distortion takes place from center G1, G2 with the contact position of two roller surface 303k, 305k.On the other hand, first member 303 and second member 305 are subjected to vertical force F1 ', F2 ' as the reaction force of above-mentioned vertical force F1, F2.Here, vertical force F1 ' has with axial vertical (making progress among Figure 19) composition with towards axial one distolateral (among Figure 19 to the right) axial composition.On the other hand, vertical force F2 ' has with axially vertical (Figure 19's is downward) composition with towards axially another is distolateral (among Figure 19 left) axial composition.As, the vertical force F1 ' that acts on first member 303 from cylindrical roller 306 has towards axial one distolateral axial composition, this axially becomes to be divided into active force of the direction of eliminating the relative displacement between first member 303 and second member 305.

And, among Figure 19, though so that second member 305 is illustrated towards axial one distolateral mobile example with respect to first member 303, but with second member 305 with respect to first member 303 under the situation of axial the other end side shifting, also identical with above-mentioned explanation, can obtain to eliminate the active force of the direction (direction opposite) of the relative displacement between first member 303 and second member 305 with the situation of above-mentioned Figure 19.Like this, force application device 301 both was set as and played a role as pressure spring, again the force application device that plays a role as the elongation spring.

And, because cylindrical roller 306 or special-shaped roller surface 303k, 305k are disposed equably around axle, therefore regardless of the relative displacement between first member 303 and second member 305, the power that acts on the square with the axis direction of each member (cylindrical roller 306, first member 303 and second member 305) all can be cancelled.Thus, first member 303 can reciprocally move relative to straight line vertically with second member 305.

As mentioned above, special-shaped roller surface 303k and special-shaped roller surface 305k are concave curved surface, and each special-shaped roller surface 303k, 305k constitute continuous smoothly curved surface.Thereby, as long as cylindrical roller 306 does not arrive adjacent roller surface position, boundary 303b, 305b each other with the contact position of roller surface 303f, 305f, then along with clamping little by little (at leisure) variation at interval of the cylindrical roller 306 of the relative displacement of first member 303 and second member 305.Like this, as mentioned above, to giving the active force of the direction of eliminating the relative displacement between two members 303,305 that produce because of relatively moving between first member 303 and second member 305 between two members 303,305.Thus, this force application device 301 becomes the replacement compression helical spring in the past or the device of elongation helical spring etc.That is to say, can be used in giving in the purposes of spring between the member that relatively moves along rectilinear direction.

According to force application device 301, can be enough do not use the simple formation of helical spring etc. to give application of force function (below be also referred to as springiness).Thereby, compare with force application component in the past can suppress to use continuously or timeliness due to aging, can realize long lifetime.

In addition, different with force application component in the past, the peripheral members such as joining portion that do not need second member that will reciprocally move relative to straight line and first member to engage with force application component.Thus, peripheral structure can be simplified, can suppress part count or assembly cost, and improve reliability, and the miniaturization of member becomes easy.

In addition, force application device 301 becomes the member of the function of the load that also has between supporting first member 303 and second member 305 (load of the direction that cylindrical roller 306 is compressed).

In addition, force application device 301 can utilize the torque load of cylindrical roller 306 supporting roles between first member 303 and second member 305.That is, in the force application device 301, be disposed at axial one distolateral 4 first line column rollers 361 and be disposed at the axially multiple row structure of another 4 distolateral secondary series cylindrical rollers 362, therefore can support above-mentioned torque load owing to be set as to have.In addition, in the force application device 301, as shown in figure 16, owing to be located in the four directions that cylindrical roller 306 between inside portion 305a and the lateral part 303a is located at inside portion 305a, so be made into to support the force application device 301 of the torque load of all directions.And the present invention is not defined in the situation that cylindrical roller 306 is 2 row as described above, both can be 1 row, can be more than 3 row yet.

In addition, in the force application device 301, compare with force application component in the past, design freedoms such as spring rigidity become high.Promptly, freely design spring rigidity etc. owing to can utilize the rigidity of design (position of curvature, centre of curvature etc.), each member of formation (cylindrical roller 306, first member 303, second member 305) of special-shaped roller surface to wait, so design freedom becomes high.Like this, even do not change the size (bodily form) of member, also can be in wide range characteristic such as setting spring rigidity.In addition, in helical spring in the past, relation between relative displacement and the spring rigidity is linear (necessarily), and in the force application device 301, also can be as make the spring rigidity freely change the spring rigidity according to relative displacement non-linearly changing etc. with respect to relative displacement.

In the force application device 301, adopt following formation, that is, and as the clamping of the cylindrical roller 306 of rolling element moving and in whole cylindrical roller 306, change equably along with member 303,305 at interval relative to straight line.If so be provided with, then the active force that acts on member 303,305 from each rolling element becomes impartial, can obtain springiness effectively.In addition, because the load that is added on each cylindrical roller 306 becomes impartial, so the life-span is elongated.

Moving allowed band (permission stroke) relative to straight line and depend on the design of special-shaped roller surface 303k, 305k and the regime of elastic deformation of rolling element 6 and each member 303,305, the scope etc. that is provided with of special-shaped roller surface 303k, 305k in the force application device of the present invention.If without limits, force application device then of the present invention as a rule can move until the free position that reaches following (a)～(c) relative to straight line aspect the power that is used to make first member 303 and 305 relative displacements of second member (below be also referred to as relative displacement power).

(a) each member 303,305 or cylindrical roller 306 reach the limit of regime of elastic deformation.

(b) cylindrical roller 306 leaves roller surface 303f, 305f, comes off from force application device 301.

(c) because of first member 303 and the 305 mutual interference of second member etc., relative displacement is restricted.

Like this, in the design process of roller surface 303f, 305f or special-shaped roller surface 303k, 305k etc., also can utilize moving between first member 303 and second member 305 that cylindrical roller 306 is moved to adjacent special-shaped roller surface relative to straight line.In the above-mentioned force application device 301 (with reference to Figure 15), if strengthen the relative displacement between first member 303 and second member 305, then first member 303 and second member 305 interfere, or cylindrical roller 306 comes off, therefore do not have cylindrical roller 306 and cross over position, boundary 303b, 305b and to adjacent special-shaped roller surface 303k, the situation that 305k moves, yet for example by (not disposing cylindrical roller 306) special-shaped roller surface 303k of a plurality of preparations is set in force application device 301 vertically continuously, 305k, and can realize the formation that cylindrical roller 306 moves to adjacent special-shaped roller surface.Under this situation, can on the relative displacement power that acts between first member 303 and second member 305, set certain limiting value.Like this, in the force application device of the present invention, can also add the function that prevents between first member 303 and second member 305, to act on excessive relative displacement power.

Among the present invention, shape of rolling element etc. is not particularly limited, so long as moving and rolling shape gets final product along with first member and second member relative to straight line.Like this, being defined in cylindrical roller unlike above-mentioned mode of execution, for example also can be ball or tapered roller, can suitably use employed roller in rolling bearing in the past.In addition, in order to improve the setting degrees of freedom of spring rigidity, also can use the hollow rolling element (for example hollow cylindrical roller or hollow ball) of easy elastic compression distortion etc.In addition, the material of rolling element can suitably be selected accordingly with desired performance in the force application device.

As mentioned above, the active force that utilizes force application device of the present invention to obtain can illustrate by the resiliently deformable of the part in the contact area of main consideration first member and second member and rolling element when rolling element relatively moves.But wall thickness that also can be by reducing first member or second member etc. increases the resiliently deformable of the macroscopic view of first member and/or second member.In addition, also can adopt following formation, that is, rolling element is resiliently deformable not basically, mainly obtains active force by first member or second component elasticity are out of shape.By add the rigidity of first member or second member as design considerations, design freedom of the present invention can further improve.

By changing wall thickness (average wall thickness), Thickness Distribution or the material of first member or second member, can change the rigidity (to the rigidity of the pushing force due to the rolling element) of first member or second member.For example, can give concavo-convexly, or make second member 305 hollow the outside of first member 303 of above-mentioned force application device 301.

As variation of the present invention, also can be following force application device.

For example, in force application device 301, also can be the formation (that is, first member 303 is only by constituting that lateral part 303a forms) of having removed bottom 303b.In addition, though in force application device 301, in the internal configurations of the lateral part of tubulose 303a inside portion 305a is arranged, yet also can not be this kind formation.It for example also can be following formation, promptly, the force application device 370 of variation as shown in figure 20, first member 303 is to have opposed mutually two outside board 303c and with they members at the approximate U font in the cross section of the linking department 303d of side's side binding, dispose the inside portion 305a of second member 305 between these two outside board 303c.Figure 20 is the axial sectional view of force application device 370, and Figure 21 is the sectional view of force application device 370 of the C-C line of Figure 20.

In addition, in the force application device 301, the sectional shape of the first roller surface 303f and the second roller surface 305f is approximate square, yet also can adopt following formation, promptly, the sectional shape of these roller surfaces 303f, 305f is made as positive n dihedrals (n is the integer more than 3) such as approximate equilateral triangle or positive pentagon, and special-shaped roller surface is set forming on each corresponding formation face of polygonal each limit with these cross sections.If so be provided with, then the first roller surface 303f, the second roller surface 305f and rolling element can be disposed equably around axle.

Though in force application device 301, the first roller surface 303f is all occupied by special-shaped roller surface 303k, yet also the part of the first roller surface 303f can be made as special-shaped roller surface 303k.Similarly, though in force application device 301, the second roller surface 305f is all occupied by special-shaped roller surface 305k, yet also the part of the second roller surface 305f can be made as special-shaped roller surface 305k.

In addition, as the example of the formation different, also can be following force application device with force application device 301.First member and second member are across the opposed tabular component of rolling element, and the opposed faces of two members is set as first roller surface and second roller surface respectively, and at least one side of these first roller surfaces and second roller surface has above-mentioned special-shaped roller surface.And, under this situation, need the support that the relative straight line with second member of first member can be supported movably.

In addition, in above-mentioned force application device 301, can only obtain active force, yet can also give rotary action power with the relative rotation (reversing) of second member 305 first member 303 along the direction that relatively moves (parallel relatively movement direction).Among special-shaped roller surface 303k, the 305k of above-mentioned mode of execution, give curvature on the relative straight line movement direction (axially) to first member 303 and second member 305, and do not give curvature on the direction to relative straight line movement direction quadrature with this.But for example also can adopt following special-shaped roller surface, promptly, by in special-shaped roller surface 303k and special-shaped roller surface 305k, except relative straight line movement direction, also give the curvature with the direction of relative straight line movement direction quadrature, thereby to giving the rotary action power of the direction of eliminating above-mentioned first member that the relative rotation because of first member 303 and second member 305 produces and the phase difference between second member between first member 303 and second member 305.Under this situation, by rolling element being made as ball (ball) etc., can also be to giving rotation urging function (torsion spring) between first member 303 and second member 305.

Claims (6)

1. pulley apparatus is used for driving by belt the subsidiary engine class of motor, and the feature of this pulley apparatus is,

Possess:

Belt pulley member cylindraceous, it is hung belt and has the outboard raceway face in interior all sides at the periphery volume;

Inner member, it has and the opposed inboard raceways face of above-mentioned outboard raceway face at outer circumferential side, and is adapted to and can rotates relatively with respect to above-mentioned belt pulley member;

Rolling element, it rollably is located between above-mentioned outboard raceway face and the above-mentioned inboard raceways face,

At least one side of above-mentioned inboard raceways face and outboard raceway face has special-shaped roller surface at least a portion, this abnormity roller surface is on one side along with above-mentioned belt pulley member makes the rolling element rolling with relative rotation between the above-mentioned inner member, reduce the clamping interval of this rolling element on one side gradually, and to giving rotary action power between above-mentioned belt pulley member and the above-mentioned inner member, this rotary action power is to eliminate the power of the direction of the above-mentioned belt pulley member that produces because of above-mentioned relative rotation and the phase difference between the above-mentioned inner member.

2. pulley apparatus according to claim 1 is characterized in that, but by on the input shaft that above-mentioned inner member one is installed on rotatably alternator and use as the pulley apparatus that alternator is used.

3. pulley apparatus according to claim 1 is characterized in that, but by above-mentioned inner member one being installed on rotatably on the bent axle and use as the pulley apparatus that bent axle is used.

4. pulley apparatus according to claim 1 is characterized in that, between above-mentioned belt pulley member and above-mentioned inner member, is folded with the rolling bearing that they can be supported mutually with the relative rotation.

5. an automatic takeup is characterized in that,

Possess:

Swing arm, its have interior all sides be formed with the tubular of outboard raceway face base end part, and extend and the belt pulley that will roll up the extension belt is fixed into the arm that rotates freely from this base end part;

Support member, it has and the opposed inboard raceways face of above-mentioned outboard raceway face at outer circumferential side, and by supporting above-mentioned base end part with the relative rotation, comes the above-mentioned swing arm of free swaying ground supporting;

Rolling element, it rollably is located between above-mentioned outboard raceway face and the above-mentioned inboard raceways face,

At least one side of above-mentioned inboard raceways face and outboard raceway face has special-shaped roller surface at least a portion, this abnormity roller surface is on one side along with above-mentioned base end part makes the rolling element rolling with relative rotation between the above-mentioned support member, reduce the clamping interval of this rolling element on one side gradually, and to the rotary action power of the direction of giving above-mentioned base end part that elimination produces because of above-mentioned relative rotation and the phase difference between the above-mentioned support member between above-mentioned base end part and the above-mentioned support member, utilize this rotary action power, with the swaying direction application of force of above-mentioned swing arm to regulation.

6. automatic takeup according to claim 6 is characterized in that, between above-mentioned base end part and above-mentioned support member, is folded with the rolling bearing that they can be supported mutually with the relative rotation.

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