JP5353869B2 - Pulley device with built-in one-way clutch for automotive auxiliary equipment - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pulley device with a built-in one-way clutch obtaining further satisfactory clutch performance by reducing friction between a spring and a retainer. <P>SOLUTION: In the pulley device, a column part 21 of the retainer 18a includes an escape part 21a cut out near a contact part 103 of the spring 100' with a roller 17, and the escape part 21a is formed being cut out to avoid a movable region of the contact part 103 of the spring 100'. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

The present invention relates to a pulley device with a built-in one-way clutch, and more particularly, to a one-way vehicle accessory used by being fixed to an input shaft of an auxiliary device such as an alternator driven by the power of an engine crankshaft. The present invention relates to a pulley device with a built-in clutch.

  2. Description of the Related Art Conventionally, various auxiliary machines are driven using a drive engine of an automobile as a drive source. For example, when driving an alternator that generates electric power necessary for an automobile, a clutch built-in type pulley apparatus incorporating a one-way clutch is used. It is known to use (see, for example, Patent Document 1).

  The one-way clutch has a cam surface on the inner ring or the outer ring so as to form a wedge space between the inner ring and the outer ring, and the locked state and the overrun state are achieved by engaging and disengaging the rollers disposed in the wedge space. repeat. Each roller arranged in the wedge space is accommodated in a plurality of pockets formed in the cage, and is elastically pressed in the direction of exerting the wedge action, that is, the lock direction, by a spring locked to the cage. Is done.

  A spring 100 shown in FIG. 17A has a base 101 and a pair of pressing portions 102 bent with respect to the base 101 on both sides of the base 101, and comes into contact with a roller at the tip of the pressing portion 102. 17B includes a base portion 101, a pair of pressing portions 102, and a pair of contact portions 103 that are bent with respect to the pressing portion 102 at the distal end portion of the pressing portion 102 and contact the roller. And have.

  For example, as shown in FIG. 18, the spring 100 ′ is locked by a center-side spring holding portion 112 and a pair of end-side spring holding portions 113 that extend radially outward from the column portion 111 of the cage 110. , Between a pair of annular portions 114 (only one annular portion is shown in the figure).

JP-A-8-61433

  By the way, as shown in FIG. 18, in the overrun state of the one-way clutch, the spring 100 ′ is bent by being pressed by the roller 120. At this time, the pressing portion 102 and the contact portion 103 of the spring 100 ′ that bends are bent. May interfere with the column part 111 of the cage 110. For this reason, it is required to suppress the interference of the spring 100 ′ with the cage 110 and reduce the friction between the spring 100 ′ and the cage 110 to obtain better clutch performance.

The present invention has been made in view of the above-described circumstances, and an object of the present invention is to incorporate a one-way clutch for an auxiliary machine of an automobile that can reduce friction between a spring and a cage to obtain better clutch performance. It is in providing a type | mold pulley apparatus.

The above object of the present invention can be achieved by the following constitution.
(1) A sleeve in which the rotation shaft is fitted, a pulley disposed concentrically with the sleeve on the radially outer side of the sleeve, and provided between the outer peripheral surface of the sleeve and the inner peripheral surface of the pulley. Only when one side tends to rotate relative to the other in a predetermined direction, between the one-way clutch that transmits the rotational force between the pulley and the sleeve, and the outer peripheral surface of the sleeve and the inner peripheral surface of the pulley. A support bearing provided at a position spaced axially with respect to the one-way clutch, and supporting a radial load applied to the pulley and enabling relative rotation between the pulley and the sleeve;
The one-way clutch includes a cage that rotates together with one member of a sleeve and a pulley, a plurality of engagement elements held by the retainer, and a spring that presses the plurality of engagement elements in a direction of engagement. ,
The cage includes a pair of annular portions, a plurality of column portions that connect the pair of annular portions, and an inner surface of the pair of annular portions that sandwich the spring separately from the cage. A pair of end-side spring holding portions provided in a portion aligned with the portion and a central-side spring holding portion provided in an axial center portion of each column portion,
The spring is a leaf spring having a base that is held between the center-side spring holding portion a pair of end-side spring holding portion, a pair of pressing portions which is bent at an acute angle relative to the base on either side of the base as a bent portion automobiles A pulley device with a built-in one-way clutch for an auxiliary machine ,
A pulley apparatus with a built-in one-way clutch for an auxiliary machine of an automobile, wherein a notch penetrating in a radial direction is provided in a pillar portion of the cage so as to avoid a movable region of a contact portion of a spring.

  According to the one-way clutch built-in pulley apparatus of the present invention, the spring is formed by a leaf spring, and the pillar portion of the cage is provided with a notch so as to avoid the movable region of the contact portion of the spring. When the spring is bent, the contact portion of the spring is prevented from interfering with the cage, and the friction between the spring and the cage can be reduced to obtain better clutch performance.

It is a longitudinal cross-sectional view of the pulley apparatus with a built-in clutch which is 1st Embodiment of this invention. FIG. 2 is a top view partially showing a cage and a spring of the one-way clutch in FIG. 1 in a circumferential direction with an outer ring removed. The spring of the one way clutch of FIG. 1 is shown, (a) is the side view, (b) is the expanded view. It is a figure which shows the front-end | tip part of the spring which concerns on the modification of the one-way clutch of 1st Embodiment. It is a figure which shows the front-end | tip part of the spring which concerns on the other modification of the one-way clutch of 1st Embodiment. FIG. 10 is a top view partially showing a cage and a spring of a one-way clutch according to a second embodiment in a circumferential direction with an outer ring removed. 6 shows a spring of the one-way clutch in FIG. 6, (a) is a side view thereof, and (b) is a developed view thereof. It is a figure which shows the front-end | tip part of the spring which concerns on the modification of the one-way clutch of 2nd Embodiment. It is a figure which shows the front-end | tip part of the spring which concerns on the other modification of the one way clutch of 2nd Embodiment. The spring of the one-way clutch of 3rd Embodiment is shown, (a) is the perspective view, (b) is the side view. The retainer of the one-way clutch of the third embodiment is shown, in which (a) is a cross-sectional view at the normal time, and (b) is a cross-sectional view at the time of maximum deformation. The spring and cage | basket at the time of the largest deformation | transformation of the cage | basket of the one-way clutch of 3rd Embodiment are shown, (a) is the sectional drawing, (b) is the XII partial enlarged view of (a). It is a perspective view which shows partially the holder | retainer and spring of the one-way clutch of 4th Embodiment of this invention in the circumferential direction. FIG. 14 is a perspective view partially showing the cage of FIG. 13 in the circumferential direction. It is a perspective view which shows partially the holder and spring which concern on the modification of the one way clutch of 4th Embodiment in the circumferential direction. It is a perspective view which shows partially the holder | retainer and spring of the one-way clutch of 5th Embodiment of this invention in the circumferential direction. It is a perspective view which shows the spring of the conventional one-way clutch. It is a perspective view which shows the holder | retainer and spring of the conventional one-way clutch.

  Hereinafter, a pulley device with a built-in one-way clutch according to each embodiment of the present invention will be described in detail with reference to the drawings.

(First embodiment)
First, with reference to FIGS. 1-3, 1st Embodiment of this invention is described in detail.
As shown in FIG. 1, the pulley apparatus 10 with a built-in clutch includes a sleeve 11 into which a rotating shaft (not shown) of an auxiliary machine such as an alternator is screwed, and a sleeve 11 radially outside the sleeve 11. And a pulley 12 having a belt groove 12a formed on the outer peripheral surface thereof. A drive belt (not shown) suspended from a drive pulley (not shown) fixed to the crankshaft of the engine is stretched over the belt groove 12a.

  In addition, a one-way clutch 13 is disposed between the outer peripheral surface of the sleeve 11 in the axial intermediate portion and the inner peripheral surface of the pulley 12 in the axial intermediate portion. A pair of rolling bearings 14 is disposed between the outer peripheral surface at both axial ends of the sleeve 11 and the inner peripheral surface at both axial ends of the pulley 12, which are spaced apart. The one-way clutch 13 transmits a rotational force between the pulley 12 and the sleeve 11 only when the pulley 12 tends to rotate relative to the sleeve 11 in a predetermined direction. As the rolling bearing 14, a deep groove ball bearing or the like is used, and the sleeve 11 and the pulley 12 can be relatively rotated while supporting a radial load applied to the pulley 12.

  The one-way clutch 13 includes an inner ring 15 that is press-fitted and fixed to the outer peripheral surface of the sleeve 11, an outer ring 16 that is press-fitted and fixed to the inner peripheral surface of the pulley 12, and between the outer peripheral surface of the inner ring 15 and the inner peripheral surface of the outer ring 16. And a plurality of rollers 17 which are engaging elements disposed in the. The outer peripheral surface of the inner ring 15 forms a cam surface in which a plurality of ramp portions 15a are formed at predetermined intervals in the circumferential direction, and the roller 17 is formed from the cylindrical surface 16a of the outer ring 16 and each ramp portion 15a. It is rotatably held in the wedge space.

  The one-way clutch 13 includes a cage 18 having a plurality of pockets for individually accommodating the rollers 17 and a spring 19 that elastically presses the rollers 17 in a direction in which the wedge space is engaged. Yes.

  As shown in FIG. 2, the retainer 18 includes a pair of annular portions 20 and a plurality of column portions 21 that connect the pair of annular portions 20.

  Protrusions (not shown) that engage with both axial ends of the lamp portion 15 a are formed on the inner peripheral surfaces of the pair of annular portions 20, and the cage 18 rotates together with the inner ring 15 and the sleeve 11. In addition, a pair of end-side spring holding portions 22 are radially outward from the outer peripheral surface side of each column portion 21 at a portion that is aligned with each column portion 21 in the circumferential direction on the inner side surface of the pair of annular portions 20. It is formed in a state of projecting. On the other hand, the center side spring holding part 23 is formed in the axial direction center part of each pillar part 21 in the state which protrudes radially outward from the outer peripheral surface side of each pillar part 21. As shown in FIG. The spring 19 is sandwiched between one circumferential side surface of the end side spring holding portion 22 and the other circumferential side surface of the center side spring holding portion 23.

  As shown in FIGS. 2 and 3, the spring 19 is a leaf spring, and bends both sides of the base portion 25, which is an intermediate portion in the longitudinal direction, at predetermined positions as bent portions (portions where maximum stress is generated) 26. The press part 27 is comprised by this, and the front-end | tip part of the press part 27 is used as the contact part 28 with which the roller 17 contacts. As a result, the spring 19 comes into contact with each roller 17 at the contact portion 28 and presses each roller 17 toward the locking direction, that is, toward the shallow side of the groove of the ramp portion 15a.

  The contact portion 28 of the spring 19 is formed so that the cage side is cut out in a rectangular shape over the pressing portion 27 and the radial width W1 thereof is smaller than the radial width W2 of the bent portion 26. Yes. Thereby, in the state where the spring 19 is disposed in the cage 18, the contact portion 28 is positioned away from the surface of the column portion 21 even when the spring 19 is bent.

  The pulley apparatus 10 with a built-in one-way clutch configured in this way has a tendency that the outer ring 16 rotates relative to the inner ring 15 in a predetermined direction when the rotational angular speed of the pulley 12 is faster than the rotational angular speed of the rotating shaft. In this case, the roller 17 is engaged with the wedge space between the cylindrical surface of the outer ring 16 and the ramp portion 15a of the inner ring 15 by the wedge action, and the rollers 17 are interposed between the outer ring 16 and the inner ring 15 via the respective rollers 17. Rotational force can be transmitted freely. As a result, the pulley 12 and the sleeve 11 cannot be rotated relative to each other (in a locked state), and the rotational force of the engine is transmitted to the rotating shaft. On the other hand, when the rotational angular velocity of the pulley 12 is slower than the rotational angular velocity of the rotating shaft, the engagement of the roller 17 is released, and the pulley 12 and the sleeve 11 can be freely rotated (overrun state).

  Here, when the roller 17 is positioned on the deep side of the groove of the ramp portion 15a of the inner ring 15 such as in an overrun state, the spring 19 is pressed and bent by the roller 17, but the roller 17 of the spring 19 Since the contact portion 28 is notched in a rectangular shape on the side of the pressing portion 27, the contact portion 28 does not interfere with the surface of the column portion 21 of the retainer 18, and reduces the friction between the spring 19 and the retainer 18. can do. Further, in the state where the spring 19 is bent, the bent portion 26 becomes a maximum stress portion where the maximum stress is generated. However, since the radial width of the bent portion 26 is kept large, the strength of the spring 19 is maintained. be able to.

  Furthermore, even when the cage 18 bends to the outer ring side due to centrifugal force, the cage 18 is prevented from interfering with the contact portion 28 of the spring 19, so that the clutch performance is impaired even in an operating environment due to high-speed rotation. It will not be.

  Therefore, according to the pulley device 10 with a built-in one-way clutch of the present embodiment, the spring 19 is formed by a leaf spring, and the spring 19 is notched in the vicinity of the contact portion with the roller 17, and the contact portion 28 with the roller 17. Since the radial width W1 is smaller than the radial width W2 of the bent portion 26, the contact of the spring 19 also occurs when the spring 19 is bent or when the cage 18 is bent toward the outer ring. Interference between the portion 28 and the cage 18 is suppressed, and friction between the spring 19 and the cage 18 can be reduced to obtain better clutch performance.

  In addition, the shape of the press part 27 of the spring 19 and the contact part 28 is not limited to the thing of this embodiment, It shows to Fig.4 (a)-(f) and Fig.5 (a)-(g). As described above, any shape may be employed as long as the radial width W1 of the contact portion 28 is smaller than the radial width W2 of the bent portion 26.

  Specifically, the pressing portion 27 and the contact portion 28 of the spring 19 may have a shape in which a corner portion 30 cut on the cage side is curved as shown in FIG. As shown in d), the radial width is gradually reduced toward the axial end surface by cutting out linearly from the cage side radial end surface toward the axial end surface, or by curving in a convex or concave shape. It may be. Further, as shown in FIGS. 4E and 4F, the pressing portion 27 and the contact portion 28 are notched in multiple stages on the cage side, and have a radial width from the bent portion 26 side toward the axial end surface. You may make it reduce gradually. Further, as shown in FIGS. 5 (a) to 5 (g), the pressing portion 27 and the contact portion 28 of the spring 19 have the features of FIGS. 3 and 4 (a) to (f) described above on the cage side. The outer ring side may be formed in the same manner, that is, the outer ring side and the cage side may be symmetrical in the radial direction. Thereby, the directionality in the radial direction of the spring 19 is lost, and the assembling property can be improved.

(Second Embodiment)
Next, a second embodiment of the present invention will be described in detail with reference to FIGS. The present embodiment is different from the first embodiment only in the shape of the spring of the one-way clutch, and other parts are the same as those in the first embodiment, and the description is omitted or simplified.

  As shown in FIGS. 6 and 7, the spring 40 of the present embodiment constitutes a pressing portion 43 by bending both sides of a base portion 41 that is a middle portion in the longitudinal direction at a predetermined position as bending portions 42. The contact portion 45 is configured by further bending the distal end portion of the pressing portion 43 as another bent portion 44 at a predetermined position.

Further, as shown in FIG. 7, the contact portion 45 of the spring 40 and the pressing portion 43 on the contact portion side are notched on the cage side, and the radial width W1 of the contact portion 45 is equal to that of the bent portion 42. It is formed so as to be smaller than the radial width W2. That is, the radial width W1 of the contact portion 45 is set to be smaller than the maximum radial width W2 of the pressing portion 43. Thus, as in the first embodiment, in the state where the spring 40 is disposed in the cage 18, the contact portion 45 is located away from the surface of the column portion 21 even when the spring 40 is bent.
Other configurations and operations are the same as those in the first embodiment.

  Also in the present embodiment, the shapes of the contact portion 45 of the spring 40 and the pressing portion 43 on the contact portion side are not limited to those of the present embodiment, and FIGS. 8A to 8G and FIGS. 9 (a) to 9 (h), any shape may be used as long as the radial width W1 of the contact portion 45 is smaller than the radial width W2 of the bent portion 42. .

  That is, as shown in FIGS. 8A to 8C, the contact portion 45 and the pressing portion 43 of the spring 40 are linear, convex, or concave and curved from the cage side radial end surface to the axial end surface. The radial width may be gradually reduced toward the axial end face. Alternatively, as shown in FIGS. 8D to 8F, the radial width is gradually reduced to the other bent portion 44 of the pressing portion 43, and the contact portion 45 has a diameter of the bent portion 42. It may be a uniform width smaller than the direction width W2. Alternatively, as shown in FIG. 8 (g), the contact portion 45 and the pressing portion 43 of the spring 40 are notched in multiple stages on the cage side, and have a radial width from the bent portion 26 side toward the axial end surface. You may make it reduce gradually. Furthermore, as shown to Fig.9 (a)-(h), the contact part 45 and the press part 43 of the spring 40 are good also considering the outer ring | wheel side and the cage | basket side as a symmetrical shape in radial direction.

(Third embodiment)
Next, a third embodiment of the present invention will be described in detail with reference to FIGS. In addition, this embodiment is characterized by the size and shape of the spring shown in FIG. 9B of the second embodiment. The same parts are denoted by the same reference numerals, and the description thereof is omitted or simplified. To do.

  That is, as shown in FIG. 10, in the spring 40 of this embodiment, the contact portion 45 and the pressing portion 43 are arranged from the radial end surface of the cage side toward the axial end surface, that is, from the taper start point 46 to the taper end point. It is formed in a taper shape that is linearly cut up to 47, gradually reducing the radial width toward the axial end face, and the outer ring side and the cage side are symmetrical in the radial direction. Here, in FIG. 10B, β represents the taper angle, B ′ represents the taper width at the taper end point 47, and C represents the taper length.

  On the other hand, the column portion 21 of the cage 18 is shown in FIG. 11B from the axial end portions connected to the pair of annular portions 20 to the axial center portion when centrifugal force due to high-speed rotation acts. Is deformed substantially linearly. In addition, the area | region in which the center side spring holding | maintenance part 23 is formed does not deform | transform substantially by thickness. Here, in FIG. 11A, L represents the length of the column part, and A represents the axial dimension of the center side spring holding part 23. FIG. 11B shows a state in which the cage 18 is most deformed. In FIG. 11B, B represents the maximum deformation amount of the cage, and α represents the deformation angle at that time.

  FIG. 12 shows the spring and the cage at the time of maximum deformation of the cage. Here, the taper width B ′ at the taper end point 47 of the spring 40 is determined in consideration of the maximum deformation amount B of the cage 18, but when the taper angle β of the spring 40 is larger than the deformation angle α of the cage 18. When the cage 18 is gradually deformed, it interferes at the position of the taper start point 46 of the spring 40 before contacting the taper end point 47 of the spring 40. For this reason, the taper shape of the spring 40 cannot be utilized to the maximum.

For this reason, in this embodiment, when the retainer 18 is deformed to the maximum deformation amount, the taper-shaped taper angle β of the spring 40 is set so as to prevent the interference between the spring 40 and the retainer 40. It is set smaller than the deformation angle α. That is,
α> β (1)

Further, the deformation angle α and the taper angle β are given as follows.
α = tan-1 (B / ((LA) / 2)) (2)
β = tan−1 (B ′ / C) (3)

Therefore, the taper length C is determined from the formulas (1) to (3) and the taper width B ′ determined in consideration of the maximum deformation amount B, and the taper shape of the spring 40 can be set. For convenience, when the taper width B ′ is the maximum deformation amount B,
tan-1 (B / ((LA) / 2))> tan-1 (B / C) (4)
And 2C> LA is set. When the spring 40 is supported only by the end side spring holding part 22, A = 0 is set.

  By setting the taper dimension of the spring 40 in this way, interference between the spring 40 and the cage 18 due to the deformation of the cage 18 can be prevented, and a reduction in the clutch function can be prevented. Moreover, since the spring 40 of this embodiment is made into a symmetrical shape in the radial direction, there is no directivity in the radial direction of the spring 40, and assemblability can be improved.

  The setting of the taper dimension of the spring 40 of this embodiment is also applicable to the spring 40 shown in FIG. 8A, and the folding shown in FIG. 4B and FIG. 5C of the first embodiment. It is applicable also to the structure which does not have a curved part.

  Further, in the present embodiment, for convenience, the calculation is performed by matching the positions of the axial end face of the spring 40 and the axial end face of the center side spring holding portion 23 of the cage 18, but when these positions do not match. Is applicable, and may be calculated based on the deformation amount of the cage 18 at the position of the axial end face of the spring 40.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described in detail with reference to FIGS.
In addition, this embodiment is characterized by the shape of the cage of the one-way clutch, and the conventional spring shown in FIG. 17B is applied. Other parts are the same as those of the first embodiment, and the description thereof is omitted or simplified.

  As shown in FIGS. 13 and 14, the retainer 18 a of this embodiment includes a pair of annular portions 20 and a plurality of column portions 21, as in the first embodiment, and a pair of annular portions 20. Convex portions 31 are formed on the inner peripheral surface of each of the two, and a pair of end-side spring holding portions 22 and a center-side spring holding portion 23 are respectively formed on the axial end portions and the axial center portion of each column portion 21. ing.

  The column portion 21 of the cage 18a has a relief portion 21a cut out in the vicinity of the contact portion 103 with the roller 17 of the spring 100 ′. The escape portion 21a is formed by cutting out so as to avoid the movable region of the contact portion 103 of the spring 100 '. In this embodiment, the escape portion 21a is circumferentially extended to the position of one side surface in the circumferential direction of the central spring holding portion 23. Notched into. The column portion 21 may be partially cut off on the outer surface side of the column portion 21 so as not to interfere with the contact portion 103 of the spring 100 ′ in the vicinity of the contact portion 103 of the spring 100 ′ with the roller 17. You may cut out entirely like the part 21a.

  Even in this embodiment in which the cage 18a is configured in this way, the spring 100 'is pressed by the roller 17 when the roller 17 is positioned on the deep side of the groove of the ramp portion 15a of the inner ring 15 in an overrun state or the like. However, since the column portion 21 of the cage 18a has the relief portion 21a, the contact portion 103 of the spring 100 'and the column portion 21 of the cage 18a do not interfere with each other, and the spring The friction between 19 and the cage 18 can be reduced. Further, even when the cage 18a is bent to the outer ring side due to the centrifugal force, the cage 18a is prevented from interfering with the contact portion 103 of the spring 100 ', so that the clutch performance can be achieved even in an operating environment due to high-speed rotation. It will not be damaged.

  Therefore, according to the pulley device 10 with a built-in one-way clutch of the present embodiment, the column portion 21 of the retainer 18a has the relief portion 21a cut out in the vicinity of the contact portion 103 with the roller 17 of the spring 100 ′. Therefore, even when the spring 100 ′ is bent or when the cage 18 a is bent toward the outer ring, the contact portion 103 of the spring 100 ′ and the cage 18 a are prevented from interfering with each other. The friction between the cages 18a can be reduced to obtain better clutch performance.

  Here, the cage 18a of the present embodiment may be used in combination with the springs of the first to third embodiments. For example, as shown in the modification of FIG. 15, the spring 40 of the second embodiment. May be used together.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described in detail with reference to FIG. This embodiment is also characterized by the shape of a one-way clutch cage, and the conventional spring shown in FIG. 17B is applied. Other parts are the same as those of the first embodiment, and the description thereof is omitted or simplified.

  As shown in FIG. 16, the retainer 18b of the present embodiment also includes a pair of annular portions 20 and a plurality of column portions 21 as in the first embodiment, and the inner circumference of the pair of annular portions 20. A convex portion (not shown) is formed on the surface, and a pair of end-side spring holding portions 22 ′ and a center-side spring holding portion 23 are respectively formed at both axial end portions and the axial center portion of each column portion 21. Yes.

  In addition, the cage 18b of the present embodiment has an annular portion 20 with a circumferential width substantially equal to the pillar portion 21 at a portion that is aligned with each pillar portion 21 in the circumferential direction on the inner surface of the pair of annular portions 20. It has a pair of rigidity increase parts 50 which have the height substantially equal to the outer peripheral surface. For this reason, the pair of end portion side spring holding portions 22 ′ are continuously formed on the inner side in the axial direction of the rigidity increasing portion 50 so as to hold the spring 100 ′ with the center side spring holding portion 23. Yes. As a result, the axial length L1 of the roller 17 is set longer than the axial length L2 of the spring 100 ', that is, the axial length of the holder 18b.

  Since the rigidity at the base portion of each column portion 21 can be improved by the pair of rigidity increasing portions 50, bending of each column portion 21 of the retainer 18b due to centrifugal force is suppressed, and the retainer 18b and Since interference with the spring 100 'is prevented, the clutch performance is not impaired, and this is particularly effective in an operating environment with high-speed rotation.

  Further, the cage 18b having the rigidity increasing portion 50 of the present embodiment may have the escape portion 21a of the fourth embodiment, and the springs 19 and 40 of the first to third embodiments are applied. Also good.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.

In the present embodiment, the inner peripheral surface of the outer ring is a cylindrical surface and the outer peripheral surface of the inner ring is a cam surface, but the inner peripheral surface of the outer ring may be a cam surface and the outer peripheral surface of the inner ring may be a cylindrical surface.
In this embodiment, the inner ring of the one-way clutch is press-fitted into the sleeve and the outer ring of the one-way clutch is press-fitted into the pulley. However, the inner ring may be formed integrally with the sleeve, or the outer ring may be formed integrally with the pulley.
In this embodiment, the pulley device with a built-in clutch is mounted between the rotating shaft of the alternator and the driven pulley. However, it may be mounted between the pulley of the starter and the rotating shaft. Only when there is a tendency to relatively rotate in a predetermined direction, the transmission of the rotational force between the sleeve and the pulley becomes free.

  Further, the spring holding method by the cage of the present invention may be held by the end side spring holding part and the center side spring holding part of the column part as in this embodiment, or provided in a pair of ring parts. It may be held by a spring holding portion.

DESCRIPTION OF SYMBOLS 10 Pulley apparatus with a built-in clutch 11 Sleeve 12 Pulley 13 One-way clutch 14 Support bearing 15 Inner ring 15a Lamp part 16 Outer ring 17 Roller 18 Cage 19,40 Spring 21 Column part 21a Escape part 26, 42 Bending part (maximum stress is generated) Part to do)
27, 43 Pressing part 28, 45 Contact part

Claims (1)

A sleeve in which a rotation shaft is fitted; a pulley disposed concentrically with the sleeve on a radially outer side of the sleeve; and provided between an outer peripheral surface of the sleeve and an inner peripheral surface of the pulley; Only when one of the sleeves tends to rotate relative to the other in a predetermined direction, a one-way clutch that transmits rotational force between the pulley and the sleeve, an outer peripheral surface of the sleeve, and the pulley A support bearing provided in a position axially separated from the inner circumferential surface with respect to the one-way clutch, and capable of rotating the pulley and the sleeve while supporting a radial load applied to the pulley; With
The one-way clutch presses a retainer that rotates together with one member of the sleeve and the pulley, a plurality of engagement elements held by the retainer, and a direction in which the engagement elements are engaged. A spring, and
The retainer includes a pair of annular portions, a plurality of column portions connecting the pair of annular portions, and an inner surface of the pair of annular portions that sandwich the spring separately from the retainer. A pair of end-side spring holding portions provided in a portion aligned with each column portion and a central-side spring holding portion provided in the axial center portion of each column portion,
The spring includes a pair of end-side spring holding portions and a base portion sandwiched between the center-side spring holding portions, and a pair of pressing portions bent at an acute angle with respect to the base portion with both sides of the base portion being bent portions. It is a pulley device with a built-in one-way clutch for automotive auxiliary equipment that is a leaf spring,
A pulley apparatus with a built-in one-way clutch for automobile auxiliary equipment , wherein a notch penetrating in a radial direction is provided in a pillar portion of the retainer so as to avoid a movable region of a contact portion of the spring. .

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