WO2017170587A1

WO2017170587A1 - Gearing

Info

Publication number: WO2017170587A1
Application number: PCT/JP2017/012721
Authority: WO
Inventors: 慎弥松岡
Original assignee: 武蔵精密工業株式会社
Priority date: 2016-03-29
Filing date: 2017-03-28
Publication date: 2017-10-05
Also published as: JP2017180558A

Abstract

This gearing has one transmission member having a first axis as the center axis, and another transmission member that can revolve around the first axis while rotating around a second axis, which is offset from the first axis. A transmission mechanism between both transmission members comprises: one transmission groove that has an annular wave shape, that is provided to the one transmission member, and that is centered around the first axis; another transmission groove that has an annular wave shape, that is provided to the other transmission member, and that is centered around the second axis; and a plurality of rolling elements that are interposed in a plurality of intersecting sections of both transmission grooves. Retention members (H1, H2) are composed of synthetic resin elements comprising: a plurality of housings (51, 52), each having a retention hole (31, 32) in the plurality of rolling elements (23, 26), and being arranged at equal intervals along the same circumference; and a plurality of rod-like linking parts (53, 54) that integrally link adjacent housings (51, 52) in the circumferential direction. This configuration makes it possible to increase transmission efficiency by ensuring the smooth rolling of all of the rolling elements by using synthetic resin elements having a specific structure as the retention members.

Description

Transmission

The present invention includes a transmission device, particularly a pair of transmission members facing each other, and a transmission mechanism provided between the transmission members and capable of transmitting torque while shifting between the transmission members. The present invention relates to a transmission device in which a transmission member has a first axis as a central axis, and the other transmission member can revolve around a first axis while rotating around a second axis that is eccentric from the first axis.

For example, as shown in FIG. 7 of Patent Document 1, the above transmission device is conventionally known. In this device, the speed change mechanism is located on the surface of one transmission member facing the other transmission member and has a first axis. A wave-shaped transmission groove centered on the other side of the other transmission member and the other transmission member on the surface facing the one transmission member and a wave-shaped ring centered on the second axis and having a different wave number from the one transmission groove Transmission grooves, a plurality of rolling elements interposed at a plurality of intersections of both transmission grooves, and a holding member (retainer) interposed between both transmission members having a holding hole for holding the rolling elements And have. And in the transmission device of this structure, there exists an advantage which can attain axial size reduction of an apparatus by forming each transmission member in plate shape, for example.

Japanese Unexamined Patent Publication No. 2010-14214

Incidentally, in the conventional transmission device shown in FIG. 7 of Patent Document 1, a plate-like shape having a plurality of holding holes for holding a plurality of rolling elements (balls) so as to be slidable between a pair of transmission members in the transmission mechanism. The holding member is interposed. The holding member has a plurality of rolling elements arranged in a pair of transmission members in a state where the plurality of rolling elements are arranged at equal intervals in the holding hole. The work of engaging the overlapping portions of the transmission grooves facing each other of the transmission members can be facilitated.

As described above, the holding member can function as an assembly jig when the apparatus is assembled. During transmission after the apparatus is assembled, the holding member rotates along the transmission grooves while rotating relative to the pair of transmission members rotating eccentrically with each other. It has been considered that a plurality of rolling elements that roll are held, causing a disadvantage that a resistance load is caused by the eccentric rotation, which reduces the transmission efficiency of the transmission device (for example, [ 0004]).

The present invention has been made in view of such circumstances, and by holding the holding member as a synthetic resin body having a specific structure, it is possible to hold the rampage when some of the rolling elements pass through the suddenly changing curvature portion of the transmission groove. It is an object of the present invention to provide a transmission device that can increase the transmission efficiency by enabling the member to effectively suppress in cooperation with other rolling elements and ensuring the smooth rolling of the entire rolling element.

In order to achieve the above object, the present invention includes a pair of transmission members facing each other, and a transmission mechanism that is provided between the transmission members and capable of transmitting torque while shifting between the transmission members. And the other transmission member can revolve around the first axis while rotating around the second axis eccentric from the first axis, and the pair of transmissions Each of the members has a transmission groove on both opposing surfaces, and the transmission mechanism is provided on the one transmission member and has one of the transmission grooves forming a corrugated ring centered on the first axis. The other transmission member, which is provided in the other transmission member and has a corrugated annular shape centering on the second axis and has a wave number different from that of the one transmission groove, the one transmission groove, and the other transmission groove Interspersed at multiple intersections, A plurality of rolling elements that perform transmission transmission between the two transmission members while rolling the groove, and a holding member that is interposed between the two transmission members and has a plurality of holding holes that hold the rolling elements. The holding member includes a plurality of housing portions each having the plurality of holding holes and arranged at intervals on the same circumference, and housing portions adjacent to each other in the circumferential direction. It is a first feature that it is composed of a synthetic resin body having a plurality of rod-like connecting portions that integrally connect each other.

According to the present invention, in addition to the first feature, the holding member is integrally connected to a hub portion located at a central portion or a radial intermediate portion thereof, and the hub portion and the plurality of housing portions. The second feature is that a plurality of spoke portions are integrally provided.

According to the present invention, in addition to the first or second feature, the cylindrical housing portion has a spherical bearing surface that rotatably fits and holds the rolling element on the inner peripheral surface of the holding hole. A third feature of the present invention is that the housing part is provided with a slit that allows the diameter of one end of the holding hole to be expanded when the rolling element is fitted to or detached from the holding hole. To do.

According to the first feature of the present invention, the holding member that is interposed between a pair of opposing transmission members and holds a plurality of rolling elements existing at the intersections between the wavy annular transmission grooves of both transmission members, A plurality of housing parts each having a holding hole and arranged on the same circumference at intervals corresponding to a plurality of rolling elements are integrally connected to each other in the circumferential direction. Since the holding member is made of a synthetic resin and the housing parts are connected to each other by the rod-shaped connecting portions. Therefore, when some rolling elements try to run out when passing through the sudden change in curvature of the transmission groove, the holding effect of the holding member itself and the holding member and other rolling elements can be reduced. Combined with the vibration suppression effect due to the cooperation of moving objects, it is effective for the violence of some rolling elements Suppressible and will, thereby, the entire plurality of rolling elements, can ensure smooth rolling along the transmission groove, it can contribute to the improvement of the transmission efficiency. In addition, the holding member can easily maintain an appropriate mutual positional relationship of the plurality of rolling elements (that is, a positional relationship corresponding to a plurality of intersections between the two transmission grooves) at the time of assembly of the transmission device, thereby improving the assembly workability. However, since the holding member can be made of a synthetic resin and reduced in weight, handling is simplified and assembly workability is further improved. According to the second feature, the holding member includes Since the hub portion located at the center portion or the intermediate portion in the radial direction and the plurality of spoke portions that integrally connect the hub portion and the plurality of housing portions are integrally provided, the holding member is made of synthetic resin. Thus, even if the rigidity of the rod-like connecting portion is insufficient, the overall rigidity and strength of the holding member can be effectively increased by the reinforcing effect of the hub and spokes, and the centrifugal force of the rolling elements and the housing portion can be increased. This makes it possible to effectively suppress the movement.

According to the third feature, the cylindrical housing portion has a spherical bearing surface on the inner peripheral surface of the holding hole for rotatably fitting and holding the rolling element. Since a slit is provided so that the diameter of one end of the holding hole can be increased when the rolling element is fitted to or detached from the holding hole, the housing part is held by utilizing the elastic deformation of the cylindrical housing part with the slit. Mounting of the rolling element into the hole is facilitated, and an assembly composed of the holding member and the plurality of rolling elements is easily obtained.

FIG. 1 is a longitudinal front view of a transmission device (differential device) according to an embodiment of the present invention. 2 is a cross-sectional view taken along line 2-2 of FIG. 3 is a cross-sectional view taken along line 3-3 of FIG. 4 is a cross-sectional view taken along line 4-4 of FIG. FIG. 5 is an enlarged cross-sectional view taken along the line 5 in FIG. FIG. 6 is a single perspective view of the first retainer. FIG. 7 is an enlarged cross-sectional view taken along the line 7 in FIG. FIG. 8 is a single perspective view of the second retainer. FIG. 9 is a single perspective view (corresponding to FIG. 6) showing a modification of the first retainer.

C ・・・・・・ Differential case (Transmission case)
D ・・・・・・ Differential device (Transmission device)
H1, H1 ', H2, .. First and second retainers (holding members)
T1, T2, ... 1st and 2nd transmission mechanism (transmission mechanism)
X1, X2 ··· First and second axis 5 ··· First transmission member (one transmission member)
6... Eccentric rotating member 8... 2nd transmission member (the other transmission member)
9 .... Third transmission member (One transmission member)
21, 25 .. 1st and 4th transmission groove (one transmission groove)
22, 24 ··· 2nd and 3rd transmission groove (the other transmission groove)
23, 26 .. First and second rolling elements (rolling elements)
31, 32 .. First and second holding holes (holding holes)
51, 52 ···

Housing portions

51s, 52s ···

Slits

53, 54 ··· Rod-like connecting portions 55, 55 '· · Hub portions 57, 57' ··· Spoke portion 61 ··· First inner peripheral surface ( Bearing surface)

Embodiments of the present invention will be described below with reference to the accompanying drawings.

First, an embodiment of the present invention shown in FIGS. 1 to 8 will be described. In FIG. 1, a differential device D as a transmission device is housed in a transmission case 1 of an automobile together with a transmission.

In the differential device D, the left and right drive axles S1, S2 (in which the rotation of the ring gear Cg that rotates in conjunction with the output side of the transmission device is arranged on the central axis of the differential device D, that is, the first axis X1, are relatively rotatable. That is, the first and second drive shafts) are distributed while allowing differential rotation between the drive axles S1 and S2. The drive axles S1, S2 and the transmission case 1 are sealed with seal members 4, 4 '.

The bottom of the mission case 1 is configured as an oil pan (not shown) that can store a predetermined amount of lubricating oil. The stored lubricating oil in the oil pan is vigorously stirred by rotating a rotating portion in the mission case 1, for example, a differential case C described later, and scattered widely in the internal space of the case 1, and the scattered lubricating oil makes the case Each part in 1, that is, a lubricated part can be lubricated. In addition to (or instead of) the above-described lubrication structure, the lubricating oil pumped by pump means such as an oil pump may be forcibly fed to each part in the mission case 1.

The differential device D includes a differential case C as a transmission case that is supported by the transmission case 1 so as to be rotatable about the first axis X1, and a differential mechanism 3 to be described later housed in the differential case C. The differential case C includes a ring gear Cg made of a helical gear having oblique teeth Cga provided on the outer periphery of a short cylindrical gear body, and a pair of left and right first and first pairs whose outer peripheral ends are joined to both axial ends of the ring gear Cg. 2 side wall parts Ca and Cb. At least one of the side wall portions Ca and Cb is provided with a drain hole (not shown) capable of appropriately discharging excess lubricating oil in the differential case C by centrifugal force or the like in the vicinity of the outer peripheral end thereof.

The first and second side wall portions Ca and Cb integrally have cylindrical first and second hubs HB1 and HB2 arranged on the first axis X1 at their inner peripheral end portions, respectively. The outer peripheral portions of HB1 and HB2 are rotatably supported by the mission case 1 via bearings 2 and 2 '. The first and second drive axles S1 and S2 are fitted and supported on the inner peripheral portions of the first and second hubs HB1 and HB2 so as to be rotatable about the first axis X1, respectively. At least one of the fitting surfaces (in the illustrated example, the inner peripheral surfaces of the hubs HB1 and HB2) includes at least the hubs HB1 and HB2 and the drive axle S1, when the automobile is moving forward (ie, when the drive axles S1 and S2 are rotating forward). Along with the relative rotation with S2, first and

second spiral grooves

18 and 19 for drawing the scattered lubricating oil in the mission case 1 into the differential case C are formed. The outer ends of the

spiral grooves

18 and 19 are opened in the mission case 1 and the inner ends thereof are opened in the differential case C, respectively.

Next, the structure of the differential mechanism 3 in the differential case C will be described with reference to FIGS.

The differential mechanism 3 is provided integrally with the first side wall portion Ca and can be rotated around the first axis X1 and is spline-fitted 16 to the first drive axle S1 to be coupled to the first axis X1. A hollow main shaft portion 6j that integrally includes a cylindrical first spline boss SB1 (that is, a first output boss) that can rotate around, and a second axis X2 that is eccentric from the first axis X1 by a predetermined eccentricity e. An eccentric rotating member 6 in which an eccentric shaft portion 6e serving as an axis is coupled and integrated, and one side portion is disposed opposite to the first transmission member 5, and the eccentric shaft portion 6e is rotatable via a bearing 7 formed of a ball bearing. An annular second transmission member 8 to be supported and a circle that is disposed opposite to the other side of the second transmission member 8 and is spline-fitted 17 to the second drive axle S2 so as to be rotatable about the first axis X1. An annular third transmission member 9 and first and second transmission members 5 A first transmission mechanism T1 which transmit the torque while shifting between 8, and a second transmission mechanism T2 which transmit the torque while shifting between the second and

third transmission members

8,9.

Thus, the second transmission member 8 is rotatably supported around the second axis X2 by the second transmission member 8 being rotatably supported on the eccentric shaft portion 6e of the eccentric rotation member 6 that rotates about the first axis X1. Can revolve around the first axis X1 relative to the main axis 6j while rotating around the second axis X2 relative to the eccentric axis 6e of the eccentric rotating member 6 around the first axis X1. .

Further, the second transmission member 8 has a ring plate-like first half 8a that is rotatably supported by the eccentric shaft portion 6e of the eccentric rotating member 6 via a bearing 7, and an interval between the first half 8a. And a ring-plate-shaped second half body 8b facing each other and a basically cylindrical connecting member 8c for integrally connecting the two

half bodies

8a and 8b. In particular, in the present embodiment, the first half 8a and the second half 8b are respectively fitted in the inner peripheral surfaces of the one end and the other end of the connecting member 8c, and the fitting portions are welded and caulked. It is fixed by suitable fixing means such as. The first transmission mechanism T1 is disposed between the opposing surfaces of the first half 8a and the first transmission member 5, and the second transmission mechanism T1 is disposed between the opposing surfaces of the second half 8b and the third transmission member 9. A transmission mechanism T2 is provided.

The connecting member 8c is provided with a plurality of first oil circulation holes 11 that communicate between the internal space IC of the differential case C and the hollow portion SP of the second transmission member 8 at equal intervals in the circumferential direction. Lubricating oil scattered in the internal space IC can be introduced into the hollow portion SP through the first oil circulation hole 11. The second half 8b is formed with a circular second oil circulation hole 12 that allows the hollow portion SP to communicate with the inner peripheral side of the second transmission mechanism T2.

The third transmission member 9 is a main shaft that integrally includes a cylindrical second spline boss SB2 (that is, a second output boss) that is spline-fitted 17 to the second drive axle S2 and is rotatable about the first axis X1. A portion 9j and a circular ring plate portion 9c concentrically connected to the inner end portion of the main shaft portion 9j and facing the second half 8b are coupled and integrated.

A first thrust washer TH1 that allows relative rotation between the inner side surface of the first side wall portion Ca of the differential case C and the eccentric rotating member 6 is interposed between the inner surface and the first spiral groove. An oil passage 41 is formed to communicate the inner end opening (i.e., outlet) of 18 with the inner peripheral side of the first transmission mechanism T1 via the back surface of the first thrust washer TH1. Lubricating oil drawn into the differential case C from the transmission case 1 by the pulling action of the first spiral groove 18 flows into the oil passage 41, and the flowing lubricating oil flows into the inner peripheral side of the first transmission mechanism T1 and the bearing. 7 is supplied.

Further, a second thrust washer TH2 that allows relative rotation between the inner side surface of the second side wall portion Cb of the differential case C and the outer side surface of the third transmission member 9 is interposed. In the second thrust washer TH2, the lubricating oil drawn into the differential case C from the transmission case 1 by the drawing action of the second spiral groove 19 is oil between the third transmission member 9 and the second side wall Cb. Supplied through line 45.

Further, the differential mechanism 3 is opposite in phase to the eccentric shaft portion 6e of the eccentric rotating member 6 and the total center of gravity G of the second transmission member 8 across the first axis X1, and larger than the rotational radius of the total center of gravity G. And a balance weight W that is attached to the main shaft portion 6j of the eccentric rotating member 6 so as not to be relatively rotatable. This balance weight W is comprised from the cyclic | annular base part Wm fixed to the main axis | shaft part 6j with the clip 10, and the weight part Ww fixed to the circumferential direction specific area | region of the cyclic | annular base part Wm. The hollow portion SP of the second transmission member 8 is used as a storage space for the balance weight W.

As shown in FIGS. 1 and 2, the first transmission member 5 has a waveform centered on the first axis X <b> 1 on the inner surface facing the one side portion (first half 8 a) of the second transmission member 8. An annular first transmission groove 21 is formed, and the first transmission groove 21 extends in the circumferential direction along a hypotrochoid curve having a virtual circle centered on the first axis X1 in the illustrated example. On the other hand, a corrugated annular second transmission groove 22 centering on the second axis X2 is formed on one side portion (first half 8a) of the second transmission member 8 facing the first transmission member 5. . In the illustrated example, the second transmission groove 22 extends in the circumferential direction along an epitrochoid curve having a virtual circle centered on the second axis X2 as a base circle, and is smaller than the wave number of the first transmission groove 21. It has a wave number and intersects the first transmission groove 21 at a plurality of locations.

The first transmission groove 21 and the second transmission groove 22 are constituted by square grooves having a U-shaped cross section as shown in FIGS. Moreover, the opposing inner side surfaces of the

respective transmission grooves

21 and 22 are expanded in a pre-expanded manner toward the open surface side of the groove with a predetermined minute taper angle α. In the case of this embodiment, since the first transmission member 5 (first side wall portion Ca) and the second transmission member 8 (first and

second half bodies

8a and 8b) are forged, the predetermined minute taper is used. The angle α is a minute angle corresponding to the draft angle set when the angular groove-shaped

transmission grooves

21 and 22 are formed during the forging process, and is preferably set within a range of 1 ° to 3 °. Set to In FIG. 5, the taper angle α is slightly exaggerated.

A plurality of first rolling elements 23 extending so as to straddle between the two

transmission grooves

21 and 22 are respectively provided at a plurality of intersecting portions (that is, overlapping portions) of the first transmission groove 21 and the second transmission groove 22. Is done. First and second end portions of each first rolling element 23 in the axial direction are fitted in the first and

second transmission grooves

21 and 22, respectively, and can roll on the inner side surfaces of both

transmission grooves

21 and 22. The rolling

parts

23a and 23b are configured, and the two rolling

parts

23a and 23b are integrally connected by an intermediate connecting part 23m described later.

Between the opposing surfaces of the first transmission member 5 and the second transmission member 8 (first half 8a), a circular ring-shaped first retainer H1 as a first holding member is interposed. The first retainer H1 includes both

transmission grooves

21 and 22 of a plurality of first rolling elements 23 (specifically, both rolling

portions

23a and 23b) present at the intersections of the first and

second transmission grooves

21 and 22. A plurality of first holding holes 31 having a circular cross section for rotatably holding the intermediate coupling portions 23m of the plurality of first rolling elements 23 are provided on the same circumference so that the engagement state can be maintained. Has at intervals.

The first and

second rolling portions

23a, 23b of the first rolling element 23 have first spherical portions r1 on the outer peripheral portion thereof that are slidably engaged with the inner surfaces of the corresponding

transmission grooves

21, 22. ing. That is, in this embodiment, each rolling

part

23a, 23b has a form in which a part of the spherical surface of the hemisphere is cut by a plane orthogonal to the axis of the first rolling element 23, and the cut surface is the first rolling element 23. Are arranged opposite to the bottom surfaces of the

transmission grooves

21 and 22.

Further, the intermediate coupling portion 23m of the first rolling element 23 includes a central enormous portion 70 having a second spherical portion r2 having a larger diameter than the first spherical portion r1 and both ends of the central enlarging portion 70. (That is, a pair of columnar projecting

shaft portions

71 and 72 integrally connected to each other). The outer peripheral surfaces of the projecting

shaft portions

71 and 72 are smoothly and continuously connected to the spherical outer peripheral surfaces of the first and

second rolling portions

23a and 23b.

As clearly shown in FIGS. 5 and 6, the first retainer H <b> 1 is equidistant in the circumferential direction corresponding to the plurality of first rolling elements 23 located at the intersections of the first and

second transmission grooves

21 and 22. A plurality of housing parts 51 arranged in a row, and a plurality of bar-like connecting parts 53 that integrally connect the housing parts 51 adjacent to each other in the circumferential direction. Each is formed in an arc shape so as to be arranged on the same circle.

The housing portion 51 is formed of a substantially cylindrical tubular body having both ends opened, and the inner surface of the tubular body serves as the first holding hole 31. Then, on the inner peripheral surface of the first holding hole 31 of the housing portion 51, the intermediate connecting portion 23m of the first rolling element 23 (specifically, the second spherical portion r2 on the outer peripheral surface of the central enlarging portion 70) is rotated. And a first inner peripheral surface 61 as a spherical bearing surface that can be swingably and elastically fitted and held, and a second inner surface that has an equal inner diameter in the entire axial direction that is continuous with the inner end of the first inner peripheral surface 61. And an inner peripheral surface 62. In order to accurately hold the intermediate connecting portion 23m (specifically, the central enlarged portion 70) by the first holding hole 31, the first inner peripheral surface 61 has a minimum diameter at both axial ends thereof. Accordingly, the intermediate connecting portion 23m can be retained and retained at both ends of the first inner peripheral surface 61 which are constricted.

A radial play 80 is set between the second inner peripheral surface 62 and one projecting shaft portion 72 of the first rolling element 23, and the first rolling element 23 is formed by the play 80. Is allowed to swing with respect to the housing portion 51. Then, the limit value of the swing angle is moderately regulated by the protrusion 72 being engaged with the second inner peripheral surface 62. Thereby, since excessive swing of the 1st rolling element 23 can be prevented reliably, the fall of the transmission efficiency resulting from excessive swing can be avoided. Thus, the second inner peripheral surface 62 and the projecting shaft portion 72 constitute a swing angle regulating means provided between the first rolling element 23 and the first holding hole 31.

Each housing part 51 is provided with a plurality of slits 51 s extending along the axial direction of the first rolling element 23 at intervals in the circumferential direction of the housing part 51. According to the special arrangement of the slits 51s, the intermediate connecting portion 23m (particularly the center) of the first rolling element 23 with respect to the first holding hole 31 (particularly the first inner peripheral surface 61 as the bearing surface) of the cylindrical housing portion 51. When fitting and detaching the second spherical surface portion r2 on the outer peripheral surface of the enormous portion 70, one end portion of the first inner peripheral surface 61 in the holding hole 31 can be expanded without difficulty (that is, the cylindrical housing portion 51). Therefore, it is possible to perform elastic deformation without difficulty in the diameter expansion direction).

In the present embodiment, the inner diameter of the first inner peripheral surface 61 in the free state of the housing portion 51 is set so that the second spherical portion r2 is elastically fitted and held on the first inner peripheral surface 61. Although it is desirable to set the diameter slightly smaller than the outer diameter of the second spherical surface portion r2, it may be set to the same diameter as necessary.

As shown in FIGS. 1 and 3, a corrugated annular third transmission groove 24 centering on the second axis X2 is formed on the other side portion (second half 8b) of the second transmission member 8. In the illustrated example, the third transmission groove 24 extends in the circumferential direction along a hypotrochoidal curve having a virtual circle centered on the second axis X2 as a base circle. On the other hand, on the surface of the third transmission member 9 facing the second transmission member 8, that is, on the inner surface of the ring plate portion 9c, a corrugated fourth transmission groove 25 centered on the first axis X1 is formed. In the illustrated example, the fourth transmission groove 25 extends in the circumferential direction along an epitrochoidal curve having a virtual circle centered on the first axis X1 as a base circle, and is smaller than the wave number of the third transmission groove 24. It has a wave number and intersects with the third transmission groove 24 at a plurality of locations. The third and

fourth transmission grooves

24 and 25 are also formed by square grooves having a U-shaped cross section similar to the first and

second transmission grooves

21 and 22 described above. The inner surfaces facing each other are also expanded in a pre-expanded manner toward the open surface side of the groove with a predetermined small taper angle α as described above.

A plurality of second rolling elements 26 are interposed at intersections (that is, overlapping portions) of the third transmission groove 24 and the fourth transmission groove 25. Each of the second rolling elements 26 extends so as to straddle between the third and

fourth transmission grooves

24, 25, and both axial ends thereof, that is, the first and second rolling

parts

26a, 26b are both. It fits in the

transmission grooves

24 and 25, respectively, and can roll on the inner surfaces of the

transmission grooves

24 and 25. Since the shape and structure of the second rolling element 26 are the same as those of the first rolling element 23 described above, further description is omitted.

Between the opposing surfaces of the second transmission member 8 (second half 8b) and the third transmission member 9, a circular ring-shaped second retainer H2 as a second holding member is interposed. The second retainer H2 has a plurality of second retainers H2 so as to maintain the engagement state of the plurality of second rolling elements 26 at the intersections of the third and

fourth transmission grooves

24, 25 with both the

transmission grooves

24, 25. A plurality of second holding holes 32 having a circular cross section for holding the intermediate coupling portions 26m of the second rolling elements 26 in a rotatable manner are provided at equal intervals on the same circumference of the second retainer H2.

The second retainer H2 has the same main part shape and structure as the first retainer H1 described above. In other words, the shapes and structures of the plurality of housing portions 52 and the rod-like connecting portions 54 of the second retainer H2 are basically the same except for the shapes and structures of the housing portions 51 and the rod-like connecting portions 53 of the first retainer H1 and the number of them. For example, the shape and structure of the second holding hole 32 on the inner periphery of each housing portion 52 are the same as those of the first holding hole 31.

Further, unlike the first retainer H1, the second retainer H2 is a linear hub that integrally connects the disk-shaped hub portion 55 located in the center portion in the radial direction and the hub portion 55 and the plurality of housing portions 52. And a plurality of spoke portions 57. The plurality of spoke portions 57 extend radially from the outer periphery of the hub portion 55 toward the plurality of housing portions 51. When the intermediate connecting portion 26m (especially the central enormous portion 70) of the second rolling element 26 is fitted to and detached from each housing portion 52 of the second retainer H2 with respect to the second holding hole 32, A plurality of slits 52 s capable of expanding the diameter of one end of the holding hole 32 (particularly the first inner peripheral surface 61 serving as a bearing surface) are provided at positions avoiding the spoke portions 57 and the rod-like connecting portions 54.

In the present embodiment, the first and second retainers H1 and H2 described above are configured as a single unit integrally molded from a synthetic resin material, whereby the plurality of

housing portions

51 and 52 and the rod-like connecting

portions

53 and 54 are formed. Each of the retainers H1 and H2 that are included can be easily integrally formed with a synthetic resin, thereby reducing the cost. Each retainer H1, H2 is divided and formed into a plurality of constituent elements using a synthetic resin material, and the constituent elements are joined together by an appropriate joining means (for example, adhesion, welding, etc.) to retain each retainer H1. , H2 can also be manufactured. Further, the main parts other than the retainers H1 and H2, for example, the differential case C, the

transmission members

5, 8, and 9, the eccentric rotating member 6 and the like of the differential device D are made of a metal material.

In the present embodiment, the first transmission member 5 (first side wall portion Ca) and the second transmission member 8 (first and

second half bodies

8a and 8b) each having the wave-shaped

annular transmission grooves

21, 22, 24, and 25. ) And the third transmission member 9 are forged and formed, but they may be formed by other forming methods using a forming die (for example, casting, sintering, etc.), and even in that case, the transmission groove The taper angle α of 21, 22, 24, 25 is a minute angle corresponding to the draft angle set when the

transmission grooves

21, 22, 24, 25 are molded in the molding process using the molding die. .

In this embodiment, the trochoid coefficients of the first and

second transmission grooves

21 and 22 and the trochoid coefficients of the third and

fourth transmission grooves

24 and 25 are set to different values.

In the present embodiment described above, the wave number of the first transmission groove 21 is Z1, the wave number of the second transmission groove 22 is Z2, the wave number of the third transmission groove 24 is Z3, and the wave number of the fourth transmission groove 25 is Z4. The first to

fourth transmission grooves

21, 22, 24, 25 are formed so that the following formula is established.
(Z1 / Z2) × (Z3 / Z4) = 2

Desirably, Z1 = 8, Z2 = 6, Z3 = 6, Z4 = 4, or Z1 = 6, Z2 = 4, Z3 = 8, and Z4 = 6, as shown in the illustrated example.

In the illustrated example, the eight-wave first transmission groove 21 and the six-wave second transmission groove 22 intersect at seven locations, and seven first rolling elements 23 at the seven intersections (overlapping portions). The six-wave third transmission groove 24 and the four-wave fourth transmission groove 25 intersect at five points, and five second rolling elements 26 at the five intersecting portions (overlapping portions). Is installed.

Thus, the first transmission groove 21, the second transmission groove 22, and the first rolling element 23 cooperate with each other and can transmit torque while shifting between the first transmission member 5 and the second transmission member 8. The third transmission groove 24, the fourth transmission groove 25, and the second rolling element 26 constitute a transmission mechanism T1 and cooperate with each other to transmit torque while shifting between the second transmission member 8 and the third transmission member 9. A possible second speed change mechanism T2 is configured.

In the present embodiment described above, the first and second transmission mechanisms T1 and T2 both constitute the transmission mechanism of the present invention. Particularly in the first speed change mechanism T1, the first transmission member 5 constitutes one transmission member, the second transmission member 8 constitutes the other transmission member, and the first transmission groove 21 constitutes one transmission groove. And the second transmission groove 22 constitutes the other transmission groove. Particularly in the second transmission mechanism T2, the third transmission member 9 constitutes one transmission member, the second transmission member 8 constitutes the other transmission member, and the fourth transmission groove 25 serves as one transmission groove. In addition, the third transmission groove 24 constitutes the other transmission groove.

Next, the operation of the embodiment will be described.

Now, for example, in a state where the eccentric rotary member 6 (and hence the eccentric shaft portion 6e) is fixed by fixing the right first drive axle S1, the ring gear Cg is driven by the power from the engine, and the differential case C and therefore the first When the transmission member 5 is rotated about the first axis X 1, the eight-wave first transmission groove 21 of the first transmission member 5 is replaced by the six-wave second transmission groove 22 of the second transmission member 8. Therefore, the first transmission member 5 drives the second transmission member 8 with a speed increasing ratio of 8/6. According to the rotation of the second transmission member 8, the six-wave third transmission groove 24 of the second transmission member 8 replaces the four-wave fourth transmission groove 25 of the ring plate portion 9 c of the third transmission member 9. Since it drives via the 2 rolling elements 26, the 2nd transmission member 8 will drive the 3rd transmission member 9 with the speed increase ratio of 6/4.

After all, the first transmission member 5 is
(Z1 / Z2) × (Z3 / Z4) = (8/6) × (6/4) = 2
The third transmission member 9 is driven with the speed increasing ratio.

On the other hand, when the differential case C (and hence the first transmission member 5) is rotated in a state in which the third transmission member 9 is fixed by fixing the left second drive axle S2, the rotational driving force of the first transmission member 5 is rotated. The second transmission member 8 rotates with respect to the eccentric shaft portion 6e (second axis X2) of the eccentric rotation member 6 by the driving reaction force of the second transmission member 8 against the stationary third transmission member 9. Revolving around the first axis X1, the eccentric shaft portion 6e is driven around the first axis X1. As a result, the first transmission member 5 drives the eccentric rotating member 6 with a double speed increasing ratio.

Thus, when the loads of the eccentric rotating member 6 and the third transmission member 9 are balanced with each other or change with each other, the amount of rotation and the amount of revolution of the second transmission member 8 change steplessly, and the eccentric rotation The average value of the rotational speeds of the member 6 and the third transmission member 9 is equal to the rotational speed of the first transmission member 5. Thus, the rotation of the first transmission member 5 is distributed to the eccentric rotation member 6 and the third transmission member 9, so that the rotational force transmitted from the ring gear Cg to the differential case C can be distributed to the left and right drive axles S1, S2. it can.

At that time, Z1 = 8, Z2 = 6, Z3 = 6, Z4 = 4, or Z1 = 6, Z2 = 4, Z3 = 8, Z4 = 6 to ensure the differential function. Simplification of the eaves structure can be achieved.

By the way, in this differential device D, the rotational torque of the first transmission member 5 is applied to the second transmission member 8 via the first transmission groove 21, the plurality of first rolling elements 23 and the second transmission groove 22, and to the second transmission member 8. The rotational torque of the second transmission member 8 is transmitted to the third transmission member 9 via the third transmission groove 24, the plurality of second rolling elements 26, and the fourth transmission groove 25, respectively. Between each of the second transmission member 8, the second transmission member 8 and the third transmission member 9, torque transmission is performed in a distributed manner at a plurality of locations where the first and second

rolling elements

23 and 26 exist. The strength and weight of each transmission element such as the first to

third transmission members

5, 8, 9 and the first and second

rolling elements

23, 26 can be increased.

Further, the differential device D can be flattened in the axial direction as much as possible by making the first to

third transmission members

5, 8, and 9 plate-like, and the first and

second transmission members

5, 8 can be made as much as possible. The first transmission member T1 when the eccentric rotation member 6 is fixed by the first transmission mechanism T1 between the two opposing surfaces and the second transmission mechanism T2 between the opposing surfaces of the second and

third transmission members

8 and 9. 5 to 3 to drive the third transmission member 9 with a double speed increasing ratio, and thus a differential device D that can be easily flattened in the axial direction can be obtained.

In the present embodiment, for example, in the first speed change mechanism T1, the first and second transmission grooves 21, which form a wave shape of the first transmission member 5 and the second transmission member 8 (that is, the first half body 8a) that face each other, 22 are each constituted by a square groove having a U-shaped cross section. On the other hand, a plurality of first rolling elements 23 interposed at the intersections of the two

transmission grooves

21 and 22 roll into the

transmission grooves

21 and 22. First and

second rolling portions

23a and 23b that have first spherical portions r1 that engage with each other on their outer peripheral portions and are fitted in both

transmission grooves

21 and 22, and both rolling

portions

23a and 23b. And an intermediate connecting portion 23m that is rotatably connected to and supported by the holding hole 31 of the first retainer H1. As a result, the contact angle β of the first rolling element 23 (that is, each of the rolling

portions

23a and 23b) with respect to the first and

second transmission grooves

21 and 22 can be set sufficiently large at or near 90 °. 5, the contact angle β is defined as a normal L passing through the contact portion t between the outer peripheral surface of the first rolling element 23 and the inner surfaces of the

transmission grooves

21 and 22, and a transmission load at the contact portion t. For example, the inner surface of the

transmission grooves

21 and 22 has a predetermined small taper angle α corresponding to the draft associated with molding as described above. Is set, the contact angle β = (90 ° −α), and when the taper angle α is zero, that is, when there is no draft as in machining of the

transmission grooves

21 and 22 by machining. , Contact angle β = 90 °.

Thus, by making the contact angle β of the first rolling element 23 with respect to the

respective transmission grooves

21 and 22 sufficiently large, the thrust load generated between the

transmission grooves

21 and 22 and the rolling element 23 can be reduced to zero or greatly reduced. Therefore, the transmission efficiency of the first transmission mechanism T1 is effectively increased, and the thrust receiving portion on the back side of the first transmission member 5 (in this embodiment, the first side wall portion of the differential case C integrated with the first transmission member 5). The load burden of Ca) can be reduced, and the differential device D can be reduced in weight and durability. Furthermore, since the opposing distance between the first and

second transmission members

5 and 8 can be freely set according to the selection of the axial length of the first rolling element 23, the

first transmission member

5 and 8 are first A sufficient installation space for the retainer H1 can be secured.

Further, when the differential device D is assembled, the first retainer H1 has an appropriate mutual positional relationship between the plurality of first rolling elements 23 (ie, a positional relationship corresponding to a plurality of intersections between the first and

second transmission grooves

21 and 22). ) Can be easily and accurately maintained and the function of the assembly jig can be achieved, so that the assembly workability of the first transmission mechanism T1 can be improved. In this embodiment, the first retainer H1 is particularly By being able to be reduced in weight as a product made of synthetic resin, handling at the time of assembling and the like becomes easier and the workability is further enhanced.

Further, in the present embodiment, the intermediate connecting portion 23m of the first rolling element 23, in particular, the central enlarged portion 70 has the second spherical portion r2 on the outer peripheral portion, and the second spherical portion r2 is rotated and necked. A plurality of housing parts 51 having first holding holes 31 that fit and hold in a swingable and elastic manner are provided in the first retainer H1. Accordingly, since the first rolling element 23 is allowed to be slightly inclined between the first and

second transmission grooves

21 and 22 in each housing portion 51, the first retainer H <b> 1 is forced from the first rolling element 23. The first retainer H1 can be prevented from receiving a large bending load, and the housing portion 51 elastically holds the intermediate connecting portion 23m of the first rolling element 23. Since the backlash between the housing portion 51 and the intermediate coupling portion 23m can be eliminated and effective for suppressing the positional deviation between the first rolling elements 23, the vibration suppressing effect between the first rolling elements 23 during transmission is obtained. Enhanced. In addition, the first retainer H1 having a plurality of housing parts 51 can be restricted in the axial position by the second spherical surface part r2 of the outer peripheral surface of the intermediate coupling part 23m of the first rolling element 23. It does not move in the direction, and the collision and rubbing with the first and

second transmission members

5 and 8 on both sides can be effectively prevented, and transmission efficiency and durability are improved.

In addition, the first rolling element 23 has an intermediate connecting portion 23m having a larger diameter than the first and

second rolling portions

23a and 23b, and the cylindrical housing portion 51 is a second portion of the intermediate connecting portion 23m. A spherical bearing surface 61 for fitting and holding the spherical portion r2 so as to be rotatable and swingable is provided on the inner peripheral surface of the first holding hole 31, and the cylindrical housing portion 51 has a first holding portion. A slit 51 s is provided that allows one end portion of the first holding hole 31 to be enlarged in diameter when the intermediate coupling portion 23 m is fitted to or detached from the hole 31. As a result, the first rolling element 23 can easily fit the large-diameter intermediate connecting portion 23m into the housing portion 51 of the first retainer H1 without being obstructed by the rolling

portions

23a and 23b. The assembly comprising the one retainer H1 and the plurality of first rolling elements 23 can be easily assembled, and the elastic support for the first rolling elements 23 by the housing portion 51 is performed accurately.

Also in the second transmission mechanism T2, the shapes and structures of the second rolling element 26, the third and

fourth transmission grooves

24 and 25, and the holding hole 32 of the second retainer H2 are the same as those of the first transmission mechanism T1. Since the rolling element 23, the first and

second transmission grooves

21, 22 and the holding hole 31 of the first retainer H1 are the same as those of the first transmission mechanism T1, the second transmission mechanism T2 is similar to the first transmission mechanism T1. The same effect is exhibited.

That is, since the contact angle β of the second rolling element 26 with respect to the third and

fourth transmission grooves

24 and 25 can be set sufficiently large, the thrust load generated between the

transmission grooves

24 and 25 and the rolling element 26 is made zero. Or the transmission efficiency of the second transmission mechanism T2 can be effectively increased, and the load on the thrust receiving portion on the back side of the third transmission member 9 (in this embodiment, the second side wall portion Cb of the differential case C) can be greatly reduced. The burden can be reduced. With respect to other functions and effects, the second transmission mechanism T2 can achieve the same functions and effects as the above-described functions and effects of the first transmission mechanism T1.

The first and second retainers H1 and H2 of the present embodiment have a plurality of housing portions 51, which are arranged at intervals in the circumferential direction corresponding to the plurality of first and second

rolling elements

23 and 26, respectively. 52 and a plurality of rod-like connecting

portions

53 and 54 that integrally connect the

housing portions

51 and 52 adjacent to each other in the circumferential direction thereof, the rod-like connecting

portions

53 and 54 are bent and deformed. Thus, the first and second retainers H1 and H2 can exhibit appropriate elasticity. And this elasticity is more fully exhibited especially in combination with the retainers H1 and H2 being made of synthetic resin. Thus, in each of the speed change mechanisms T1 and T2, some of the plurality of rolling elements 23 (26) pass through the sudden curvature change portions of the transmission grooves 21, 22 (24, 25). When the rampage is about to occur, the buffering effect of the retainer H1 (H2) itself and the vibration suppression effect by the cooperation of the retainer H1 (H2) and the other rolling elements 23 (26) are combined. It is possible to effectively suppress the ramping of the rolling elements 23 (26) of the part.

In particular, the second retainer H2 includes a hub portion 55 located in the center thereof and a plurality of spoke portions 57 that integrally connect the hub portion 55 and the plurality of housing portions 52, respectively. The reinforcement effect by the portion 55 and the spoke portion 57 can sufficiently compensate for the insufficient rigidity of the rod-like connecting portion 54, and the overall rigidity strength of the second retainer H2 can be effectively increased. Thereby, the movement by the centrifugal force of the 2nd rolling element 26 and the housing part 52 can be suppressed effectively.

Furthermore, in the present embodiment, the opposing inner surfaces of the

transmission grooves

21, 22, 24, and 25 are expanded in a pre-expanded manner toward the open surface side of the groove with a predetermined minute taper angle α. , While significantly reducing the thrust load generated between the rolling

elements

23 and 26 and the

transmission grooves

21 and 22; 24 and 25, the rolling

elements

23 and 26 with respect to the

transmission grooves

21 and 22; Thrust direction positioning can be performed accurately, and it is effective in preventing the axial play and vibration of the rolling

elements

23 and 26. Moreover, since the cross-sectional shape of each of the

transmission grooves

21, 22, 24, 25 can be formed in a substantially U-shape, the forming accuracy of each of the

transmission grooves

21, 22, 24, 25 (and hence the

transmission elements

23, 26 and the transmission) The accuracy of the contact angle β with the

grooves

21, 22; 24, 25 is easily increased, and the above-described thrust load is stabilized.

By the way, in above-mentioned embodiment, although the hub part 55 and the spoke part 57 for reinforcement were provided only in the 2nd retainer H2 among 1st, 2nd retainers H1, H2, the 1st retainer H1 was shown. Depending on the arrangement configuration of other functional components (for example, the eccentric rotating member 6) located on the radially inner side (that is, the first retainer H1 and the other functional components do not interfere with each other), You may make it provide the hub part and spoke part for reinforcement also on the 1 retainer H1 side.

FIG. 9 shows an example (ie, a modified example) of the first retainer in that case. The first retainer H1 ′ includes an annular hub portion 55 ′ positioned in the radial intermediate portion thereof, and the hub portion 55 ′. And a plurality of spoke portions 57 ′ that integrally connect the plurality of housing portions 52 together. The spoke portion 57 'is formed shorter than the spoke portion 57 of the second retainer H2 because the hub portion 55' has a larger diameter than the hub portion 55 of the second retainer H2.

Thus, the first retainer H1 'of this modification can also exhibit the same function and effect as the second retainer H2, that is, the first retainer H1' has the above-described hub portion 55 'and Since the reinforcing effect of the spoke portion 57 ′ can compensate for the lack of rigidity of the rod-like connecting portion 53 and the overall rigidity of the first retainer H1 ′ can be effectively increased, the first rolling element 23 and the housing portion 51 are improved. The movement due to the centrifugal force can be effectively suppressed. Further, since the hub portion 55 ′ has an annular shape with a relatively large diameter, even when another functional component (for example, the eccentric rotating member 6) exists on the radially inner side, the hub portion 55 ′ and the other portion It is possible to avoid interference with the functional parts relatively easily.

The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

For example, in the above embodiment, the differential device D is exemplified as the transmission device, and the power input from the power source to the differential case C (first transmission member 5) is transmitted via the first and second transmission mechanisms T1 and T2. Although the first and second drive axles S1 and S2 (drive shafts) are distributed while allowing differential rotation, the present invention can be implemented in various transmission devices other than the differential gear. is there. For example, the casing corresponding to the differential case C of the above embodiment is a fixed transmission case, one of the first and second drive axles S1, S2 is an input shaft, and one of the other is an output shaft. The differential device D of the embodiment can be diverted as a transmission (decelerator or speed increaser) that can change (decelerate or increase speed) the rotational torque input to the input shaft and transmit it to the output shaft. In such a case, such a transmission (reduction gear or speed increaser) is the transmission device of the present invention. In this case, the transmission may be a transmission for a vehicle or a transmission for various mechanical devices other than the vehicle.

Moreover, in the said embodiment, although the differential device D as a transmission device is accommodated in the vehicle-mounted mission case 1 for motor vehicles, the differential device D is not limited to the differential device for motor vehicles. It can also be implemented as a differential for various mechanical devices.

In the above embodiment, the differential device D as a transmission device is applied to the left and right wheel transmission systems to distribute power while allowing differential rotation to the left and right drive axles S1, S2. However, in the present invention, a differential device as a transmission device is applied to a front / rear wheel transmission system in a front / rear wheel drive vehicle to allow power to be driven while allowing differential rotation with respect to front and rear drive wheels. May be distributed.

Moreover, although the 1st transmission member 5 of the said embodiment showed what was integrally formed with the differential case C (1st side wall part Ca) as a transmission case, the 1st transmission member 5 was made into a separate component from the differential case C, You may connect this to the differential case C so that it may rotate integrally.

Moreover, although the 2nd transmission member 8 of the said embodiment was comprised from the 1st,

2nd half bodies

8a and 8b and the connection member 8c, the 2nd transmission member 8 is one surface of one plate-shaped member. Alternatively, the second transmission groove 22 may be provided, and the third transmission groove 24 may be provided on the other surface.

Moreover, in the said embodiment, although each

transmission groove

21,22; 24,25 of 1st, 2nd transmission mechanism T1, T2 is made into the corrugated cyclic | annular wave groove along a trochoid curve, these transmission grooves are embodiment. For example, it is good also as a wave-shaped wave groove | channel along a cycloid curve.

In the above-described embodiment, the eccentric rotating member 6 and the third transmission member 9 are connected to the drive axles S1 and S2 supported by the differential case C (spline fittings 16 and 17), and the drive axles S1 and S2 are interposed therebetween. In the present invention, the eccentric rotation member 6 and the third transmission member 9 may be directly supported by the differential case C.

In the above-described embodiment, the first and second retainers H1, H1 ′, H2 as the holding members are integrally connected by the rod-like connecting

portions

53, 54 that are curved in an arc shape between the plurality of

housing portions

51, 52. However, the shape of the rod-like connecting

portions

53 and 54 is not limited to the above-described embodiment, and may be formed in a straight rod shape, for example.

In the above-described embodiment, the second retainer H2 as the holding member is reinforced with the hub portion 55 and the spoke portion 57 integral with the second retainer H2. However, the selection of the constituent material of the second retainer H2 and the rod-like connecting portion 54 are exemplified. When the required rigidity and strength of the second retainer H2 can be ensured by the structure, the hub portion 55 and the spoke portion 57 may be omitted from the second retainer H2.

Further, in the first retainer H1 ′ according to the modified example (FIG. 9), the hub portion 55 ′ has an annular shape, but other functional parts (for example, the eccentric rotating member 6) are provided on the radially inner side of the first retainer H1 ′. ) Does not exist, the hub portion 55 'of the first retainer H1' may be formed in a disk shape like the hub portion 55 of the second retainer H2.

In the above-described embodiment, the transmission device includes two transmission mechanisms (that is, the first and second transmission mechanisms T1 and T2). However, the present invention provides a transmission device including one or more transmission mechanisms. Is also applicable. In addition, the present invention can be applied to at least one speed change mechanism among a plurality of speed change mechanisms included in the transmission, for example, one of the first speed change mechanism T1 and the second speed change mechanism T2 of the embodiment. The present invention may be applied only to the speed change mechanism.

Claims

A transmission mechanism (T1) provided between a pair of transmission members (5, 9; 8) facing each other and both transmission members (5, 9; 8) and capable of transmitting torque while shifting between the transmission members (5, 9; 8). , T2), one transmission member (5, 9) having the first axis (X1) as the central axis, and the other transmission member (8) decentered from the first axis (X1). Revolving around the first axis (X1) while rotating around the two axes (X2),
The pair of transmission members (5, 9; 8) have transmission grooves (21, 22, 25, 24) on opposite surfaces of both of them,
The transmission mechanism (T1, T2) is provided on the one transmission member (5, 9) and has one of the transmission grooves (21, 25) having a corrugated ring centered on the first axis (X1); The other transmission groove (22, 22) provided on the other transmission member (8) has a corrugated annular shape around the second axis (X2) and has a wave number different from that of the one transmission groove (21, 25). 24), and the one transmission groove (21, 25) and the other transmission groove (22, 24) are interposed at a plurality of intersections, and both the transmission grooves (21, 22, 25, 24) A plurality of rolling elements (23, 26) that perform transmission transmission between the two transmission members (5, 9; 8) while rolling, and a plurality of holding holes (31, 26) that hold the rolling elements (23, 26) 32) and holding members (H1, H1 ', interposed between the two transmission members (5, 9, 8). 2) and a transmission having a,
The holding member (H1, H1 ′, H2) includes a plurality of housing portions (51, 52) each having the plurality of holding holes (31, 32) and arranged on the same circumference at intervals. And a plurality of rod-like connecting portions (53, 54) for integrally connecting the housing portions (51, 52) adjacent to each other in the circumferential direction. Transmission device.
The holding member (H1 ′, H2) includes a hub portion (55 ′, 55) positioned at the center portion or a radial intermediate portion thereof, the hub portion (55 ′, 55), and the plurality of housing portions ( The transmission device according to claim 1, characterized in that a plurality of spoke portions (57 ', 57) for integrally connecting between the first and second portions (51, 52) are integrally provided.
The cylindrical housing part (51, 52) has a spherical bearing surface (61) that fits and holds the rolling elements (23, 26) in a rotatable manner on the inner periphery of the holding hole (31, 32). The holding holes (31, 52) are provided on the housing portions (51, 52) when the rolling elements (23, 26) are fitted to and detached from the holding holes (31, 32). 32) A transmission device according to claim 1 or 2, wherein a slit (51s, 52s) is provided to enable the one end of 32) to expand in diameter.