WO2020136856A1

WO2020136856A1 - Clutch

Info

Publication number: WO2020136856A1
Application number: PCT/JP2018/048396
Authority: WO
Inventors: 栄弥大池; 忠彦加藤
Original assignee: 株式会社ユニバンス
Priority date: 2018-12-28
Filing date: 2018-12-28
Publication date: 2020-07-02
Also published as: JPWO2020136856A1

Abstract

Provided is a clutch with which shock can be suppressed when engagement occurs. The clutch (10) is equipped with a first member (20) having a first surface (21), a second member (50) having a second surface (51) opposing the first surface (21) in an axial direction, and a switching device (60) for enabling the transmission of torque. The first member (20) has a plurality of first holes (22) formed on the first surface (21), and a first engagement element (40) is swingably arranged in the first holes (22). The second member (50) has a plurality of second holes (52) formed on the second surface (52), and when torque is transmitted the first engagement element (40) engages the first holes (22) and the second holes (52). The number Ne of first engagement elements (40) that are engaged when torque is transmitted is 1, and the number Nn of second holes (52) is not divisible by the number Np of arranged first engagement elements (40).

Description

clutch

The present invention relates to a clutch that transmits and cuts off torque.

A first member having a plurality of engaging elements arranged on a first surface intersecting the axis, a second member having a plurality of holes formed on a second surface facing the first surface in the axial direction, and torque transmission There is known a clutch including a switching device that changes a state in which the torque is cut off to a state in which torque can be transmitted (Patent Documents 1 and 2). In the techniques disclosed in Patent Documents 1 and 2, when the switching device is actuated, the engaging element arranged in the first member engages with the hole of the second member, and then the first member and the second member are separated from each other. Torque is transmitted to.

Japanese Patent No. 5145019 Japanese Patent No. 6209608

However, in the above conventional technique, since there is a distance between the holes formed in the second member, when the engaging element cannot be engaged in a certain hole, the engaging element reaches the next engaging hole. , The first member rotates relative to the second member. If the relative acceleration of the first member during this period is large, the speed difference between the first member and the second member at the time of engagement becomes large, and thus the shock at the time of engagement becomes large. A technology for suppressing this shock is required.

The present invention has been made to meet this demand, and an object thereof is to provide a clutch capable of suppressing shock at the time of engagement.

To achieve this object, a clutch according to the present invention includes a first member having a first surface that intersects with an axis, a second member having a second surface that faces the first surface in the axial direction, and torque transmission. And a switching device that brings the torque around the axis line into a state in which the torque around the axis can be transmitted between the first member and the second member. The first member has a plurality of first holes formed on a first circumference centered on the axis of the first surface, and the first engaging element is swingably arranged in each of the first holes. The second member has a plurality of second holes formed on a second circumference centered on the axis of the second surface, and when transmitting torque, the first engaging element has the edge of the first hole and the second hole. Engage the respective edges of the. The number Ne of the first engaging elements engaged when transmitting torque is 1, and the number Nn of the second holes is a number that is not divisible by the number Np of the first engaging elements arranged on the first circumference. is there.

According to the clutch of claim 1, the number Ne of the first engaging elements engaged when transmitting torque is 1, and the number Nn of the second holes is the first number arranged on the first circumference. The number is not divisible by the number Np of engaging elements. Thereby, the angle at which the first member relatively rotates until the first engaging element reaches the engageable hole is set to be smaller than the central angle of the arc between the edge portions of the adjacent second holes and the edge portions of the second holes. Can be made smaller. Accordingly, even if the relative acceleration of the first member is large, it is possible to prevent the speed difference between the first member and the second member at the time of engagement from occurring easily. Therefore, the shock at the time of engagement can be suppressed.

According to the clutch of claim 2, the radially outwardly facing surface and the radially inwardly facing surface formed on each of the first member and the second member are directly or via the bearing by the contact portion. Touch each other. Since the contact portion receives the reaction force in the rotational direction and the radial direction generated between the first member and the second member when the first engaging element is engaged, the stress can be reduced. Therefore, in addition to the effect of claim 1, the durability of the clutch can be secured.

According to the clutch described in claim 3, the edge portions of the first hole are arranged at equal intervals on the first circumference, and the edge portions of the second hole are arranged at equal intervals on the second circumference. Therefore, in addition to the effects of the first or second aspect, the angle at which the first member cannot rotate but is relatively rotated can be reduced at an arbitrary position.

According to the clutch described in claim 4, the first member has a plurality of third holes formed on the first circumference of the first surface, and the second engaging element is swingably arranged in each of the third holes. To be done. The second engagement element engages with the edge portion of the third hole and the edge portion of the second hole by rotation in a direction opposite to the rotation direction in which the first engagement element engages. The number Nf of the second engaging elements engaged when transmitting the torque is smaller than the number Nq of the second engaging elements arranged on the first circumference, and the number Nn is a number that is not divisible by the number Nq. In addition to the effect of any one of items 1 to 3, it is possible to suppress a shock at the time of engaging the second engaging element.

According to the clutch of claim 5, the first member has the plurality of third holes formed on the third circumference of the first surface having a diameter different from that of the first circle about the axis. The second member has a plurality of fourth holes formed on the fourth circumference of the second surface having a diameter different from the diameter of the second circle about the axis. The second engaging element is swingably arranged in each of the third holes, and the second engaging element is rotated in a direction opposite to the rotation direction in which the first engaging element engages, and the second engaging element and the fourth hole are rotated. Engage the respective edges of the. The number Nf of the second engaging elements engaged when transmitting torque is smaller than the number Nq of the second engaging elements arranged on the third circumference, and the number Nm of the fourth holes is not divisible by the number Nq. Since it is a number, in addition to the effect according to any one of claims 1 to 3, it is possible to suppress a shock at the time of engaging the second engaging element.

It is sectional drawing of the clutch in 1st Embodiment. FIG. 2 is a sectional view of the clutch taken along the line II-II in FIG. 1. It is a front view of a 2nd member. (A) is a sectional view of the clutch taken along line IVa-IVa in FIG. 2, and (b) is a sectional view of the clutch that transmits torque. (A) is a schematic diagram showing a positional relationship between the first member and the second member, (b) is a schematic diagram showing another positional relationship between the first member and the second member, (C) is a schematic diagram which shows the positional relationship of the clutch in a comparative example, (d) is a schematic diagram which shows another positional relationship of the clutch in a comparative example. It is sectional drawing of the clutch in 2nd Embodiment. FIG. 7 is a sectional view of the clutch taken along the line VII-VII in FIG. 6. FIG. 8 is a sectional view of the clutch taken along the line VIII-VIII in FIG. 6. (A) is a schematic diagram of the clutch into which the torque of the 1st direction was input, (b) is a schematic diagram of the clutch into which the torque of the 2nd direction was input. (A) is a schematic diagram showing a positional relationship between the first member and the second member, (b) is a schematic diagram showing another positional relationship between the first member and the second member, (C) is a schematic diagram which shows the positional relationship between the 1st member and the 2nd member of the clutch in 3rd Embodiment, (d) is another position between the 1st member and the 2nd member. It is a schematic diagram which shows a relationship.

Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings. First, the schematic configuration of the clutch 10 will be described with reference to FIG. 1 is a sectional view including the axis O of the clutch 10 in the first embodiment, and FIG. 2 is a sectional view of the clutch 10 taken along the line II-II in FIG. The clutch 10 includes a first member 20, a second member 50, and a switching device 60 that rotate about an axis O. In the present embodiment, the input shaft 11 and the output shaft 12 are arranged on the same axis O, the first member 20 is coupled to the input shaft 11 (driving side), and the second member 50 is the output shaft 12 (driven side). Are bound to.

The first member 20 is a member formed in an annular shape centered on the axis O, and has a first hole in a flat surface-shaped first surface 21 that intersects the axis O (orthogonal to the axis O in the present embodiment). 22 and a plurality of third holes 25 (see FIG. 2) are formed. The first surface 21 faces the second flat surface 51 of the second member 50 in the direction of the axis O. A third surface 28 facing the second member 50 side is formed in each of the first hole 22 and the third hole 25. On the bottom surfaces 29 of the first hole 22 and the third hole 25, which are located farther from the second member 50 than the third surface 28, the oil that opens to the end surface 30 of the first member 20 on the opposite side of the first surface 21. A hole 31 is formed.

The first engaging element 40 is arranged on the third surface 28 of the first hole 22, and the second engaging element 43 is arranged on the third surface 28 of the third hole 25 (see FIG. 2 ). The compression springs 46 are arranged between the bottom surface 29 of the first hole 22 and the first engaging element 40, and between the bottom surface 29 of the third hole 25 and the second engaging element 43, respectively. The compression spring 46 urges the first engagement element 40 and the second engagement element 43 toward the second member 50 side. A retainer 47 that contacts the first engaging element 40 and the second engaging element 43 is arranged on the first surface 21 of the first member 20.

The second member 50 is a member formed in an annular shape centered on the axis O, and has a second hole in the flat surface-shaped second surface 51 that intersects the axis O (orthogonal to the axis O in the present embodiment). A plurality of 52 are formed. The 2nd hole 52 is a site|part which the 1st engaging element 40 and the 2nd engaging element 43 (refer FIG. 3) arrange|positioned at the 1st member 20 engage.

FIG. 3 is a front view of the second member 50. A plurality of second holes 52 (ten in the present embodiment) are formed in the second member 50 at intervals in the circumferential direction. The second holes 52 have the same size, and have a substantially rectangular shape when viewed from the direction of the axis O. The

edge portions

53 and 54 of the second hole 52, which are opposed to each other in the circumferential direction, are located on the circumference of the second circle 55 centered on the axis O. In the second member 50, a ring groove 56 that connects the second holes 52 in the circumferential direction is formed on the second surface 51. The second member 50 has a plurality of pin holes 57 communicating with the groove bottom of the ring groove 56.

Return to FIG. 1 to explain. The pin hole 57 opens in the end surface 58 of the second member 50 opposite to the second surface 51. The switching device 60 includes a ring 61, a pin 62, a plate member 63, and an actuator 64. The ring 61 is housed in the ring groove 56 (see FIG. 3), and the pin 62 is housed in the pin hole 57. The pin 62 transmits the force of the actuator 64 in the direction of the axis O to the ring 61 via the annular plate member 63 arranged around the output shaft 12. The actuator 64 moves the ring 61 in the direction of the axis O via the plate member 63 and the pin 62.

The clutch 10 is provided with

contact portions

34 and 37. The contact portion 34 has an annular first portion 35 integrally formed with the first member 20 with a radial distance from the outer surface 50a of the second member 50 facing outward in the radial direction, and the first portion. The bearing 36 is provided with an inner surface 35 a facing the inner side in the radial direction of 35 and an outer surface 50 a of the second member 50. The bearing 36 may be a rolling bearing, a sliding bearing, or the like. The inner surface 35a of the first portion 35 and the outer surface 50a of the second member 50 are in contact with each other via a bearing 36. The bearing 36 and the inner surface 35a of the first portion 35 may be in contact with each other via an oil film. Similarly, the bearing 36 and the outer surface 50a of the second member 50 may be in contact with each other via an oil film.

The contact portion 37 is provided inside the contact portion 34 in the radial direction. The contact portion 37 includes an annular second portion 38 integrally formed on the inner periphery of the first member 20 and an annular third portion 39 integrally formed on the inner periphery of the second member 50. There is. The outer surface 38a of the second portion 38 facing the outer side in the radial direction and the inner surface 39a of the third portion 39 facing the inner side in the radial direction are in direct contact with each other via an oil film.

As shown in FIG. 2, the first member 20 has first holes 22 and third holes 25 arranged alternately in the circumferential direction. The first hole 22 and the third hole 25 have a substantially rectangular shape when viewed from the direction of the axis O. In the present embodiment, the circumferential length of the first hole 22 is longer than the circumferential length of the third hole 25. The first member 20 has recesses 24 formed on both sides in the radial direction from one circumferential edge 23 of the first hole 22 and formed in the first surface 21, and one circumferential edge of the third hole 25. Recesses 27 extending from the portion 26 to both sides in the radial direction are formed in the first surface 21. In the present embodiment, the circumferential length of the recess 24 is longer than the circumferential length of the recess 27. A plurality of (four in this embodiment) the first holes 22 are arranged at equal intervals around the axis O, and a plurality (four in this embodiment) of the third holes 25 are arranged at equal intervals around the axis O. Has been done.

The edge portion 23 of the first hole 22 and the edge portion 26 of the third hole 25 are located on the circumference of the first circle 32 centered on the axis O. The diameter of the first circle 32 is the same as the diameter of the second circle 55 (see FIG. 3). In the first member 20, a circular groove 33 that connects the first hole 22 and the third hole 25 in the circumferential direction is formed on the first surface 21. The groove 33 is a recess into which the ring 61 arranged in the second member 50 (see FIG. 1) enters.

The first engaging element 40 is arranged in the first hole 22, and the second engaging element 43 is arranged in the third hole 25. The first engagement element 40 includes a rectangular plate-shaped support column 41 and arms 42 that project from the ends of the support column 41 to both sides in the width direction of the support column 41. The second engagement element 43 includes a rectangular plate-shaped support column 44, and arms 45 that project from the ends of the support column 44 to both sides in the width direction of the support column 44. The 1st engaging element 40 and the 2nd engaging element 43 are the same components except the direction of the peripheral direction arrange|positioned at the 1st member 20.

The arm 42 of the first engaging element 40 is accommodated in the recess 24, and the arm 45 of the second engaging element 43 is accommodated in the recess 27. Since the circumferential lengths of the first hole 22 and the recess 24 are longer than the circumferential lengths of the support column 41 and the arm 42 of the first engaging element 40, the first engaging element 40 moves inside the first hole 22. Can slide in any direction.

The retainer 47 is a disk-shaped member, and a plurality of radially extending first arms 48 and second arms 49 are alternately arranged in the circumferential direction. The retainer 47 is biased in the first direction (direction of arrow F) about the axis O by the restoring force of a compression spring (not shown) arranged in the first member 20. With the retainer 47 being biased in the first direction (direction of arrow F), the first arm 48 abuts on the circumferential end surface of the support column 41 of the first engaging element 40, and the second arm 49 is the second engaging element. A part of the column 44 of 43 is covered.

4A is a sectional view of the clutch 10 taken along the line IVa-IVa in FIG. 2, and FIG. 4B is a sectional view of the clutch 10 that transmits torque. 4(a) and 4(b), a state in which the second surface 51 of the second member 50 faces the first surface 21 of the first member 20 is illustrated for ease of explanation.

The compression spring 46 arranged between the first engaging element 40 arranged on the third surface 28 of the first hole 22 and the bottom surface 29 of the first hole 22 is the arm 42 of the support column 41 of the first engaging element 40. An elastic force (restoring force) is applied to a portion opposite to the portion provided with (see FIG. 2). In the present embodiment, the compression spring 46 is a torsion coil spring. The first arm 48 of the retainer 47 (see FIG. 2) is pressed against the end surface of the strut 41 on the arm 42 side of the first engaging element 40, and the arm 42 of the first engaging element 40 is the second member 50 of the second member 50. Since it is pressed by the surface 51, the first engaging element 40 can swing around the arm 42.

However, when the ring 61 of the switching device 60 (see FIG. 1) has entered the second hole 52, the first engaging element 40 cannot hit the ring 61 and engage with the second hole 52. Further, even if the switching device 60 is actuated and the ring 61 moves out of the second hole 52, the first member 20 moves in the second direction (counter arrow F with respect to the second member 50) as shown in FIG. Direction), the first engagement element 40 cannot engage with the second hole 52. At this time, the second engaging element 43 cannot enter the second hole 52 because the second arm 49 of the retainer 47 partially covers the support column 44.

On the other hand, when the first member 20 rotates relative to the second member 50 in the first direction (direction of arrow F), the switching device 60 is actuated to retract the ring 61 from the second hole 52. The first engaging element 40 rises up and can enter the second hole 52. Then, the first arm 48 is pushed by the first engaging element 40, and the retainer 47 rotates in the second direction (counter arrow F direction). As a result, as shown in FIG. 4B, the first engaging element 40 pushes the retainer 47 away and engages with the edge portion 23 of the first hole 22 and the edge portion 53 of the second hole 52, respectively. As a result, the first member 20 and the second member 50 integrally rotate in the first direction (direction of arrow F) and transmit torque.

The second arm 49 of the retainer 47 pushed away by the first engaging element 40 cannot cover the second engaging element 43, so that the second engaging element 43 rises toward the second member 50 side by the elastic force of the compression spring 46. Since the second hole 52 of the second member 50 is formed at a position where the second engaging element 43 raised to the second member 50 side can enter, the second engaging element 43 has the second hole 52 of the second member 50. Enter. Accordingly, when the first member 20 relatively rotates in the second direction (counter arrow F direction) with respect to the second member 50, the second engagement element 43 causes the edge portion 26 of the third hole 25 and the second hole 52. The first member 20 and the second member 50 rotate integrally with each other by engaging with the respective edge portions 54, and transmit torque.

Here, since there is a distance in the circumferential direction between the second hole 52 formed in the second member 50 and the second hole 52, the first member 20 moves in the first direction (arrow F) with respect to the second member 50. When the first engaging element 40 cannot engage with the second hole 52 at a certain timing when the first engaging element 40 reaches the second hole 52 that can be engaged next, The first member 20 rotates relative to the member 50. If the relative acceleration of the first member 20 during this period is large, the speed difference between the first member 20 and the second member 50 at the time of engagement becomes large. As a result, there is a problem that the shock at the time of engagement becomes large.

To solve this problem, it is effective to reduce the relative rotation angle of the first member 20 before the first engaging element 40 reaches the position of the second hole 52 that can be engaged next. If this angle can be made small, even if the relative acceleration is large, the speed difference between the first member 20 and the second member 50 at the time of engagement can be made less likely to occur, and the shock at the time of engagement can be suppressed. ..

A state in which torque is transmitted between the first member 20 and the second member 50 will be described with reference to FIG. FIG. 5A is a schematic view showing the positional relationship between the first member 20 and the second member 50, and FIG. 5B is another position between the first member 20 and the second member 50. It is a schematic diagram which shows a relationship. FIG. 5C is a schematic diagram showing the positional relationship of the clutch 200 in the comparative example, and FIG. 5D is a schematic diagram showing another positional relationship of the clutch 200 in the comparative example.

5A and 5B show the circumference of the first circle 32 of the first surface 21 (first member 20) and the second circle 55 of the second surface 51 (second member 50). It is the figure expanded to each line segment. The points on both ends of each line segment indicate the same points on the circumference. The circumference of the first circle 32 has the same length as the circumference of the second circle 55.

The first member 20 moves relative to the second member 50 in the first direction (direction of arrow F). In the second holes 52 (Nn=10) arranged at equal intervals on the circumference of the second circle 55, the first engaging elements 40 (Np=3) arranged at equal intervals on the circumference of the first circle 32. If any of the above) is matched, torque is transmitted between the first member 20 and the second member 50 by the first engaging element 40. Further, when any of the second engaging elements 43 (Nf=3) arranged at equal intervals on the circumference of the first circle 32 matches the second hole 52 (Nn=10), the second engaging element 43. Thus, torque is transmitted between the first member 20 and the second member 50.

As shown in FIG. 5A, in the clutch 10, one of the three first engaging elements 40 coincides with the second hole 52 (Ne=1). When the first engaging element 40 cannot engage with the second hole 52 at this timing, the first member 20 moves relative to the second member 50 in the first direction (direction of arrow F). Then, as shown in FIG. 5B, another one of the first engaging elements 40 coincides with the second hole 52. The angle R at which the first member 20 relatively moves from the timing shown in FIG. 5A to the timing shown in FIG. 5B is represented by the equation (1).

R(°)=360°/(Nn·Np/Ne) Equation (1)
In the present embodiment, Np=3, Ne=1, and Nn=10. Therefore, substituting them into the equation (1) results in R1=12°.

On the other hand, in the clutch 200 in the comparative example shown in FIG. 5C, the four first engaging elements 40 are arranged at equal intervals on the circumference of the first circle 32 of the first member 210 (Np= 4). Twelve second holes 52 are formed at equal intervals on the circumference of the second circle 55 of the second member 220 (Nn=12). In the clutch 200, all of the four first engaging elements 40 match the second holes 52 (Ne=4). When the first engaging element 40 cannot engage with the second hole 52 at this timing, the first member 210 moves in the first direction with respect to the second member 220 by the distance (R2=30°) between the second holes 52. When relatively moved (in the direction of arrow F), as shown in FIG. 5D, all of the first engaging elements 40 coincide with another second hole 52.

In the clutch 200 of the comparative example, the number Ne of the first engaging elements 40 engaged when transmitting the torque is the same as the number Np of the first engaging elements 40, so the first engaging element 40 has the second hole 52 at a certain timing. When the first member 210 cannot be engaged with the first member 210, the next timing at which the first member 210 can be engaged is when the first member 210 rotates relative to the second member 220 by the distance between the second holes 52. If the relative acceleration of the first member 20 during this period is large, the speed difference between the first member 20 and the second member 50 at the time of engagement becomes large, and thus the shock at the time of engagement becomes large.

On the other hand, in the clutch 10, the number Ne of the first engaging elements 40 engaged when transmitting torque is 1, and the number Nn (=10) of the second holes 52 is not divisible by the number Np (=3). Is set to. As a result, the angle R at which the first member 20 relatively rotates until the first engaging element 40 reaches the second hole 52 that can be engaged next, the distance between the second holes 52 (the edge 53 of the adjacent second holes 52. And the edge 53 of the second hole 52). Accordingly, even if the acceleration of the first member is large, it is possible to prevent the speed difference between the first member 20 and the second member 50 during engagement from occurring easily. Therefore, the shock at the time of engagement can be suppressed.

Also, Np (=3) and Nn (=10) are numbers that do not have a common divisor other than 1, so the number Ne of the first engaging elements 40 that engages when transmitting torque can be set to 1. As a result, the dimensional tolerances of the first member 20, the second member 50, and the first engaging element 40 are reduced as compared with the case where the clutch is manufactured so that the plurality of first engaging elements 40 are simultaneously engaged when transmitting torque. Can be relaxed.

In the clutch 10, the edge portions 23 of the first holes 22 are arranged at equal intervals on the circumference of the first circle 32, and the edge portions 53 of the second hole 52 are arranged at equal intervals on the circumference of the second circle 55. Therefore, the angle R relative to the rotation of the first member 20 can be reduced at an arbitrary position.

In the clutch 10, the number Nf (=1) of the second engaging elements 43 engaged when transmitting torque is smaller than the number Nq (=3) of the arranged second engaging elements 43, and the second hole 52 is provided. The number Nn (=10) is set to a number that is not divisible by the number Nq. Therefore, when torque is transmitted between the first member 20 and the second member 50 by the second engagement element 43, the shock at the time of engagement can be similarly suppressed.

The

contact portions

34, 37 receive a reaction force in the rotational direction and the radial direction generated between the first member 10 and the second member 50 when the first engagement element 40 and the second engagement element 43 are engaged. Since the

contact portions

34 and 37 can reduce the stress generated in the first member 10 and the second member 50, the durability of the clutch 10 can be ensured.

Next, the second embodiment will be described. In the first embodiment, the case where the first engaging element 40 and the second engaging element 43 are arranged on the circumference of the first circle 32 of the first member 20 has been described. On the other hand, in the second embodiment, the first engaging element 89 is arranged on the circumference of the first circle 85 of the first member 80, and on the circumference of the third circle 88 having a size different from that of the first circle 85. A case where the second engaging element 90 is arranged will be described. The same parts as those in the first embodiment are designated by the same reference numerals, and the following description will be omitted. FIG. 6 is a sectional view including the axis O of the clutch 70 in the second embodiment.

As shown in FIG. 6, the clutch 70 is a device for transmitting or disconnecting torque between the input shaft 11 and the output shaft 12. The clutch 70 includes a first member 80 connected to the output shaft 12, a second member 100 connected to the input shaft 11, and a switching device 120. The first member 80 is arranged inside the cylindrical portion 112 of the second member 100. The movement of the first member 80 in the axial direction with respect to the second member 100 is restricted by the restricting member 113 fixed to the cylindrical portion 112. The first surface 81 of the first member 80 is a flat surface orthogonal to the axis O. The first surface 81 faces the second surface 101 of the second member 100 in the axial direction.

FIG. 7 is a sectional view of the clutch 70 taken along the line VII-VII in FIG. The first member 80 is a substantially annular member that is coupled to the output shaft 12 by a spline. The first member 80 has a plurality of bottomed first holes 82 and third holes 86 formed on the first surface 81. A third surface 84 (see FIG. 9A) facing the second member 100 side is formed in each of the first hole 82 and the third hole 86. The first hole 82 and the third hole 86 have the same shape as the third hole 25 described in the first embodiment.

The edge portion 83 of the first hole 82 is located on the circumference of the first circle 85 centered on the axis O. The edge portion 87 of the third hole 86 is located on the circumference of the third circle 88 centered on the axis O. The diameter of the third circle 88 is smaller than the diameter of the first circle 85. The first engaging element 89 is arranged in the first hole 82, and the second engaging element 90 is arranged in the third hole 86. In the present embodiment, four first engaging elements 89 and four second engaging elements 90 are arranged (Np=Nq=4).

The first engaging element 89 and the second engaging element 90 are the same parts as each other except that they are arranged in the first member 80 in the circumferential direction, and are the same as the first engaging element 40 described in the first embodiment. It is a part of. The first engagement element 89 and the second engagement element 90 are urged toward the second member 100 side by the compression springs 91 and 92 (see FIG. 1) arranged in the first hole 82 and the third hole 86, respectively. .. In this embodiment, the compression springs 91 and 92 are torsion coil springs.

FIG. 8 is a sectional view of the clutch 70 taken along the line VIII-VIII in FIG. The second member 100 is a member formed in an annular shape centered on the axis O and has a flat surface-shaped second surface 101 that intersects with the axis O (orthogonal to the axis O in the present embodiment). A plurality of holes 102 and fourth holes 107 are formed. The second hole 102 is a part where the first engaging element 89 is engaged, and the fourth hole 107 is a part where the second engaging element 90 is engaged.

A plurality of second holes 102 (9 in the present embodiment) are formed in the second member 100 at intervals in the circumferential direction (Nn=9). The second holes 102 have the same size and are arranged at equal intervals. One edge 103 of the second hole 102 located in the circumferential direction is located on the circumference of the second circle 104 with the axis O as the center. The diameter of the second circle 104 is the same as the diameter of the first circle 85. In the second member 100, a ring groove 105 that connects the second holes 102 in the circumferential direction is formed on the second surface 101. The second member 100 is formed with a plurality of pin holes 106 communicating with the groove bottom of the ring groove 105. The pin hole 106 penetrates the second member 100 in the thickness direction (axial direction).

A plurality of (four in the present embodiment, nine) fourth holes 107 are formed in the second member 100 at intervals in the circumferential direction (Nm=9). The fourth holes 107 have the same size and are arranged at equal intervals. One edge portion 108 of the fourth hole 107 located in the circumferential direction is located on the circumference of the fourth circle 109 centered on the axis O. The diameter of the fourth circle 109 is the same as the diameter of the third circle 88. In the second member 100, a ring groove 110 that connects the fourth hole 107 in the circumferential direction is formed on the second surface 101. The second member 100 is formed with a plurality of pin holes 111 communicating with the groove bottom of the ring groove 110. The pin hole 111 penetrates the second member 100 in the thickness direction (axial direction).

Return to FIG. 6 to explain. The clutch 70 is provided with a contact portion 71. The contact portion 71 includes an annular first portion 72 integrally formed on the inner periphery of the first member 80 and an annular second portion 73 integrally formed on the inner periphery of the second member 100. There is. The outer surface 72a of the first portion 72 that faces the outer side in the radial direction and the inner surface 73a of the second portion 73 that faces the inner side in the radial direction are in direct contact with each other via an oil film.

The switching device 120 includes

rings

121 and 122, pins 123 and 124, and a cam mechanism 130. The

rings

121 and 122 are housed in the

ring grooves

105 and 110, respectively, and the

pins

123 and 124 are housed in the pin holes 106 and 111, respectively. The

pins

123 and 124 transmit the force of the cam mechanism 130 to the

rings

121 and 122. The

rings

121 and 122 regulate the swing of the first engagement element 89 and the second engagement element 90.

The cam mechanism 130 includes a first cam 131 arranged in the axial direction with respect to the first engaging element 89, a second cam 133 arranged in the axial direction with respect to the second engaging element 90, the first cam 131 and the second cam 133. And a third cam 135 opposed to. A plurality of first balls 138 are interposed between the first cam 131 and the third cam 135, and a plurality of second balls 139 are interposed between the second cam 133 and the third cam 135.

The first cam 131 is an annular member that is arranged on the opposite side of the first member 80 with the second member 100 sandwiched between them and surrounding the input shaft 11. The first cam 131 rotates integrally with the cylindrical portion 112 due to the engagement of the cylindrical portion 112 and the spline formed on the first cam 131, and is movable inside the cylindrical portion 112 in the axial direction with respect to the cylindrical portion 112. It is located in. The first cam 131 has a cam groove 132 that opens to the opposite side of the second member 100. The cam grooves 132 are, for example, grooves having a triangular cross section and extending in the radial direction, and a plurality of cam grooves 132 are provided at intervals in the circumferential direction.

The second cam 133 is an annular member that is arranged on the opposite side of the first member 80 with the second member 100 interposed therebetween and on the inner side (axis O side) of the first cam 131. The second cam 133 surrounds the input shaft 11. The second cam 133 rotates integrally with the input shaft 11 due to the engagement of the splines formed on the input shaft 11 and the second cam 133, and is movable outside in the axial direction with respect to the input shaft 11. It is located in. The second cam 133 is movable in the axial direction with respect to the first cam 131. The second cam 133 is formed with a cam groove 134 that opens to the opposite side of the second member 100. The cam grooves 134 are, for example, grooves having a triangular cross section and extending in the radial direction, and a plurality of cam grooves 134 are provided at intervals in the circumferential direction.

The third cam 135 is an annular member that faces the first cam 131 and the second cam 133. The third cam 135 surrounds the input shaft 11. The third cam 135 is rotatably arranged inside the cylindrical portion 112 with respect to the input shaft 11 and the cylindrical portion 112. The movement of the third cam 135 in the axial direction to the side opposite to the second member 100 is restricted. The third cam 135 is formed with

cam grooves

136 and 137 opening to the second member 100 side. The cam groove 136 is provided at a position facing the cam groove 132 of the first cam 131, and the cam groove 137 is provided at a position facing the cam groove 134 of the second cam 133. The

cam grooves

136 and 137 are, for example, grooves having a triangular cross section that extend in the radial direction.

A phase difference in the rotation direction is provided between the first cam 131 and the second cam 133 and the third cam 135. The first cam 131, the second cam 133, and the third cam 135 can relatively rotate while receiving the reaction force of the first ball 138 and the second ball 139 by the phase difference. When the first ball 138 or the second ball 139 engages with the first cam 131 or the second cam 133 and the third cam 135 by the relative rotation of the first cam 131 and the second cam 133 and the third cam 135, The first cam 131 or the second cam 133 and the third cam 135 rotate integrally. Since the movement of the third cam 135 in the axial direction is restricted, when a rotation difference occurs between the first cam 131 and the second cam 133 and the third cam 135, the first cam 131 or the second cam 133 is moved in the axial direction. (Toward the first member 80 side).

The operation of the clutch 70 will be described with reference to FIG. FIG. 9A is a schematic diagram of the clutch 70 in which the torque in the first direction (direction of arrow F) is input to the input shaft 11. FIG. 9B is a schematic diagram of the clutch 70 in which the torque in the second direction (direction of arrow R) is input to the input shaft 11.

As shown in FIG. 9A, the first engagement element 89 and the second engagement element 90 are biased toward the second member 100 side by compression springs 91 and 92, respectively. By rotating the first ball 138 between the cam groove 132 of the first cam 131 and the cam groove 136 of the third cam 135 that rotate integrally with the input shaft 11 in the first direction (direction of arrow F), the cam groove The first cam 131 moves away from the second member 100 by engaging with 132 and 136. On the other hand, since the cam groove 134 of the second cam 133 is out of phase with the cam groove 132 of the first cam 131, the reaction force of the second ball 139 between the third cam 135 and the second cam 133 causes The second cam 133 approaches the second member 100.

The second cam 133 pushes the pin 124 toward the first member 20 side against the elastic force of the compression spring 92, and the ring 122 pushed by the pin 124 moves the second engaging element 90 to the third member 80 of the first member 80. It is accommodated in the hole 86. Since the second engagement element 90 cannot swing into the fourth hole 107, torque transmission by the second engagement element 90 is blocked.

On the other hand, the first engaging element 89 urged by the compression spring 91 swings to enter the second hole 102. When the first engaging element 89 engages with the edge portion 83 of the first hole 82 and the edge portion 103 of the second hole 102, torque in the first direction (direction of arrow F) is applied from the second member 100 to the first member 80. Transmitted.

From this state, when the rotation of the input shaft 11 becomes slower or the rotation of the output shaft 12 becomes faster and the rotation speed of the first member 80 becomes higher than the rotation speeds of the first cam 131 and the second cam 133, the first engaging element Since 89 cannot engage with the second hole 102, torque transmission is cut off.

As shown in FIG. 9B, the second ball 139 between the cam groove 134 of the second cam 133 and the cam groove 137 of the third cam 135 that rotate integrally with the input shaft 11 moves in the second direction (arrow). By rotating in the R direction), the

cam grooves

134 and 137 are engaged, and the second cam 133 moves away from the second member 100. On the other hand, since the cam groove 132 of the first cam 131 is out of phase with the cam groove 134 of the second cam 133, the reaction force of the first ball 138 between the third cam 135 and the first cam 131 causes The 1-cam 131 approaches the second member 100.

The first cam 131 pushes the pin 123 toward the second member 100 side against the elastic force of the compression spring 91, and the ring 121 pushed by the pin 123 moves the first engaging element 89 to the first member 80 of the first member 80. It is accommodated in the hole 82. Since the first engagement element 89 cannot swing into the first hole 82, the torque transmission by the first engagement element 89 is blocked.

On the other hand, the second engaging element 90 biased by the compression spring 92 swings to enter the fourth hole 107. When the second engaging element 90 engages with the edge portion 87 of the third hole 86 and the edge portion 108 of the fourth hole 107, the second engaging element 90 moves from the second member 100 to the first member 80 in the second direction (arrow). The torque in the R direction) is transmitted.

From this state, when the rotation of the input shaft 11 becomes slower or the rotation of the output shaft 12 becomes faster and the rotation speed of the first member 80 becomes higher than the rotation speeds of the first cam 131 and the second cam 133, the second engaging element Since 90 cannot engage with the fourth hole 107, torque transmission is cut off.

A state in which torque is transmitted between the first member 80 and the second member 100 will be described with reference to FIGS. 10(a) and 10(b). FIG. 10A is a schematic diagram showing the positional relationship between the first member 80 and the second member 100, and FIG. 10B is another position between the first member 80 and the second member 100. It is a schematic diagram which shows a relationship. 10A and 10B show the circumferences of the first circle 85 of the first surface 81 (first member 80) and the second circle 104 of the second surface 101 (second member 100). It is the figure expanded to each line segment. The points on both ends of each line segment indicate the same points on the circumference. The second member 100 moves relative to the first member 80 in the first direction (direction of arrow F).

As shown in FIG. 10A, in the clutch 70, one of the four first engaging elements 89 matches the second hole 102 (Ne=1). When the first engaging element 89 cannot engage with the second hole 102 at this timing, the second member 100 moves relative to the first member 80 in the first direction (direction of arrow F). Then, as shown in FIG. 10B, another one of the first engaging elements 89 coincides with the second hole 102. In the present embodiment, Np=4, Ne=1, and Nn=9, so substituting them into the equation (1) results in R3=10°.

Similarly, in the second engagement element 90, one of the four second engagement elements 90 matches the fourth hole 107 (Ne=1). When the second engagement element 90 cannot engage with the fourth hole 107 at this timing, the second member 100 moves relative to the first member 80 in the second direction (counter arrow F direction). Then, another one of the second engaging elements 90 coincides with the fourth hole 107. In the present embodiment, Nq=4, Nf=1, Nm=9, so when these are substituted into the equation (2), R=10°.

R(°)=360°/(Nm·Nq/Nf) Equation (2)
Also in the second embodiment, the number Ne of the first engaging elements 89 engaged when transmitting torque is 1, and the number Nn of the second holes 102 is set to a number that is not divisible by the number Np. Similar to the first embodiment, it is possible to suppress shock at the time of engagement.

Further, the number Nf of the second engaging elements 90 engaged when transmitting torque is smaller than the number Nq of the second engaging elements 90, and the number Nm of the fourth holes 107 is a number that cannot be divided by the number Nq. Similar to the case of the engagement element 89, it is possible to suppress the shock when the second engagement element 90 is engaged. Further, since the number Nf is 1, compared to the case where the clutch is manufactured so that the plurality of second engaging elements 90 are simultaneously engaged when transmitting the torque, the first member 80, the second member 100, and the second engaging element. The dimensional tolerance of 90 can be relaxed.

A third embodiment will be described with reference to FIGS. 10(c) and 10(d). In the clutch 140 according to the third embodiment, ten second holes 102 are formed in the second member 100 and ten fourth holes 107 are formed in the second member 100, and the first engaging element 89 and the second engaging member are provided. The clutch 70 is the same as the clutch 70 described in the second embodiment, except that seven compound pieces 90 are arranged at equal intervals. FIG. 10C is a schematic view showing the positional relationship between the first member 80 and the second member 100 of the clutch 140 in the third embodiment, and FIG. 10D is the first member 80 and the second member 100. FIG. 8 is a schematic diagram showing another positional relationship with the member 100.

As shown in FIG. 10C, in the clutch 140, one of the seven first engaging elements 89 matches the second hole 102 (Ne=1). When the first engaging element 89 cannot engage with the second hole 102 at this timing, the second member 100 moves relative to the first member 80 in the first direction (direction of arrow F). Then, as shown in FIG. 10D, another one of the first engaging elements 89 coincides with the second hole 102. In the present embodiment, Np=7, Ne=1, and Nn=10. Therefore, when these are substituted into the equation (1), R4≈5°.

Also in the third embodiment, the number Ne of the first engaging elements 89 engaged when transmitting torque is 1, and the number Nn of the second holes 102 is a number that is not divisible by the number Np. Similarly, shock at the time of engagement can be suppressed.

The number Nf (=1) of the second engaging elements 90 engaged when transmitting torque is smaller than the number Nq (=7) of the second engaging elements 90, and the number Nm (=10) of the fourth holes 107. ) Is a number that is not divisible by the number Nq, so that it is possible to suppress a shock when the second engaging element 90 is engaged, as in the case of the first engaging element 89.

The contact portion 71 receives a rotational and radial reaction force generated between the first member 80 and the second member 100 when the first engagement element 89 and the second engagement element 90 are engaged. Since the contact portion 71 can reduce the stress generated in the first member 80 and the second member 100, the durability of the clutch 70 can be ensured.

Although the present invention has been described above based on the embodiments, the present invention is not limited to the above embodiments, and various improvements and modifications are possible without departing from the spirit of the present invention. It can be easily guessed. For example, the numbers and shapes of the first

engaging elements

40 and 89 and the second

engaging elements

43 and 90, and the numbers and shapes of the

second holes

52 and 102 and the fourth hole 107 are examples and can be set appropriately.

In the first embodiment, the case where the first member 20 is the driving side and the second member 50 is the driven side has been described, but the present invention is not limited to this. Of course, it is possible to set the first member 20 as the driven side and the second member 50 as the driving side. Similarly, in the second embodiment, the first member 80 can be the driving side and the second member 100 can be the driven side.

In the embodiment, the case of the two-way clutch including the first

engaging elements

40 and 89 and the second

engaging elements

43 and 90 has been described, but the present invention is not limited to this. Of course, it is possible to omit the second

engaging elements

43 and 90 to form a one-way clutch.

In the first embodiment, the case where the retainer 47 that restricts the rising of the second engagement element 90 is arranged has been described, but the present invention is not limited to this, and the retainer 47 can be omitted as a matter of course. When the retainer 47 is omitted, the circumferential length of the first hole 22 is shortened so that the first engaging element 40 cannot slide in the first hole 22, and the third hole on the circumference of the first circle 32 is removed. The first hole 22 is formed in the center between the hole 25 and the third hole 25. That is, the first hole 22 and the third hole 25 can be arranged at equal intervals around the axis O.

In the embodiment, the case where the torsion coil springs are used as the compression springs 46, 91, 92 has been described, but the present invention is not limited to this. Instead of the torsion coil spring, it is naturally possible to use another compression spring such as a compression coil spring.

In the first embodiment, the switching device 60 that makes the torque transmission possible by using the actuator 64 has been described, and in the second embodiment, the switching device 120 that makes the torque transmission possible by using the cam mechanism 130 has been described. .. However, it is not necessarily limited to this. For the switching device 60, a known mechanism can be appropriately set.

In the embodiment, the case where the

switching device

60, 120 restricts the swing of the first engaging

element

40, 89 and the second

engaging element

43, 90 via the

rings

61, 121, 122 and the

pins

62, 123, 124. Although explained, it is not necessarily limited to this. By omitting the

rings

61, 121, 122 and changing the tip shapes of the

pins

62, 123, 124 and the shapes of the first engaging element and the second engaging element, the first engaging element and the second engaging element via the pin. It is, of course, possible to regulate the swing of the. Further, instead of the pin or ring, a plate-like shutter or the like for preventing the first engaging element and the second engaging element from entering the

second holes

52, 102 and the fourth hole 107 is provided, and this is used as a switching device. Of course, it is possible to be a part.

In the embodiment, the case where the first

engaging elements

40, 89 and the second

engaging elements

43, 90 have the same size and shape has been described, but the present invention is not limited to this. It is of course possible that the lengths, widths, and thicknesses of the first

engaging elements

40, 89 and the second

engaging elements

43, 90 are different from each other.

In the embodiment, the case where the plurality of first

engaging elements

40 and 89 are arranged at equal intervals around the axis O has been described, but the present invention is not necessarily limited to this. It is naturally possible to make the intervals around the axis O of the first

engaging elements

40, 89 different from each other. Similarly, it is naturally possible to make the intervals around the axis O of the second

engaging elements

43, 90 different from each other.

In the embodiment, the case where the first engaging elements 40 and the second engaging elements 43 have the same number and the first engaging elements 89 and the second engaging elements 90 have the same number has been described, but the present invention is not limited to this. is not. It is of course possible to make the number of the first engaging elements 40 different from the number of the second engaging elements 43, or the number of the first engaging elements 89 and the number of the second engaging elements 90.

In the first embodiment, the case where the

contact portions

34 and 37 are provided has been described, but the present invention is not limited to this. For example, it is naturally possible to omit one of the

contact portions

34 and 37. Further, it is naturally possible to omit the bearing 36 arranged in the contact portion 34 and directly contact the inner surface 35a and the outer surface 50a via the oil film. It is of course possible to arrange a bearing in the contact part 37 like the contact part 34.

In the second embodiment, the case where the contact portion 71 is provided has been described, but it is not necessarily limited to this. It is of course possible to provide another contact portion on the outer side in the radial direction with respect to the contact portion 71. In the second embodiment, it is naturally possible to dispose the bearing on the contact portion 71 as in the first embodiment.

10, 70, 140

Clutch

20,80

First member

21,81

First surface

22,82

First hole

23,83

Edge portion

25,86

Third hole

26,87

Edge portion

32,85

First circle

34,37, 71 Contact part 36

Bearing

40,89

1st engaging element

43,90 2nd engaging element 50,100 2nd member 51,101 2nd surface 52,102 2nd hole 53,54,103 Edge part 55,104

2nd circle

60, 120 Switching device 107 Fourth hole 108 Edge portion 109 Fourth circle O axis

Claims

A first member having a first surface intersecting the axis;
A second member having a second surface facing the first surface in the direction of the axis;
A switching device that brings the torque around the axis line between the first member and the second member from the state where the torque transmission is cut off, the clutch comprising:
The first member has a plurality of first holes formed on a first circumference centered on the axis of the first surface,
A first engaging element is swingably disposed in each of the first holes,
The second member has a plurality of second holes formed on a second circumference centered on the axis of the second surface,
When transmitting torque, the first engaging element engages with the edge portion of the first hole and the edge portion of the second hole,
The number Ne of the first engaging elements engaged when transmitting torque is 1,
The clutch in which the number Nn of the second holes is a number that is not divisible by the number Np of the first engaging elements arranged on the first circumference.
The radial surface facing outward and the radial surface facing each other, which are formed on each of the first member and the second member, are provided with contact portions that come into contact with each other directly or through a bearing. clutch.
The edge portions of the first hole are arranged at equal intervals on the first circumference, and the edge portions of the second hole are arranged at equal intervals on the second circumference. The described clutch.
The first member has a plurality of third holes formed on the first circumference of the first surface,
A second engaging element is swingably disposed in each of the third holes,
The second engagement element engages with an edge portion of the third hole and an edge portion of the second hole by rotation in a direction opposite to a rotation direction in which the first engagement element engages,
The number Nf of the second engaging elements engaged when transmitting torque is smaller than the number Nq of the second engaging elements arranged on the first circumference,
The clutch according to claim 1, wherein the number Nn is a number that is not divisible by the number Nq.
The first member has a plurality of third holes formed on a third circumference of the first surface having a diameter different from that of the first circle about the axis.
The second member has a plurality of fourth holes formed on a fourth circumference of the second surface having a diameter different from that of the second circle about the axis.
A second engaging element is swingably disposed in each of the third holes,
The second engagement element engages with the edge portion of the third hole and the edge portion of the fourth hole by rotation in a direction opposite to the rotation direction in which the first engagement element engages,
The number Nf of the second engaging elements engaged when transmitting torque is smaller than the number Nq of the second engaging elements arranged on the third circumference,
The clutch according to any one of claims 1 to 3, wherein the number Nm of the fourth holes is a number that is not divisible by the number Nq.