WO2017170588A1 - Engrenage - Google Patents

Engrenage Download PDF

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Publication number
WO2017170588A1
WO2017170588A1 PCT/JP2017/012722 JP2017012722W WO2017170588A1 WO 2017170588 A1 WO2017170588 A1 WO 2017170588A1 JP 2017012722 W JP2017012722 W JP 2017012722W WO 2017170588 A1 WO2017170588 A1 WO 2017170588A1
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WO
WIPO (PCT)
Prior art keywords
transmission
axis
rolling
grooves
groove
Prior art date
Application number
PCT/JP2017/012722
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English (en)
Japanese (ja)
Inventor
慎弥 松岡
Original Assignee
武蔵精密工業株式会社
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Application filed by 武蔵精密工業株式会社 filed Critical 武蔵精密工業株式会社
Publication of WO2017170588A1 publication Critical patent/WO2017170588A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/04—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion
    • F16H25/06—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members

Definitions

  • 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.
  • the above transmission device is conventionally known.
  • 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.
  • 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.
  • both transmission grooves are formed in a V-shaped cross section or a Gothic arch shape, while the rolling elements are formed of balls. Therefore, during transmission, a large thrust load is generated between each transmission groove and the ball, which increases the frictional force between the transmission groove and the ball, or a thrust receiving portion that is in sliding contact with the rotating transmission member and its back surface.
  • the transmission device is a differential device, the frictional force between the transmission device and the transmission device is increased, thereby reducing transmission efficiency and forcing reinforcement of the thrust receiving portion.
  • a contact angle of the ball with respect to the transmission groove that is, a direction in which the ball acts on the transmission groove (in other words, a straight line (normal line) from the ball center to the contact point of the ball and the transmission groove) It is conceivable to set a large angle between the direction of the thrust and the direction of the thrust component of the load). In this case, however, another inconvenience may occur as follows.
  • the contact angle is set large, the thrust load can be reduced.
  • the contact angle is set larger, the depth of penetration of the ball into the transmission groove becomes deeper, and the two transmission members face each other. Since the interval is narrow, it is difficult to secure an installation space for the holding member that holds the plurality of balls.
  • the present invention has been made in view of such circumstances, and the thrust load between the transmission groove and the rolling element during transmission is made zero or sufficiently reduced, while sufficient installation space for the holding member is provided between the two transmission members. It is an object of the present invention to provide a transmission device that can be secured.
  • 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.
  • 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 in the groove, and a plurality of holding holes that hold the rolling elements at intervals in the circumferential direction, are interposed between the two transmission members.
  • the rolling element has a first spherical surface portion that engages with both the transmission grooves so as to be capable of rolling, and is fitted into both the transmission grooves.
  • the first and second rolling parts, and an intermediate connecting part that integrally connects the two rolling parts and is rotatably fitted and supported in the holding hole are provided as a first feature. .
  • the intermediate connecting portion of the rolling element has a second spherical portion on an outer peripheral portion, and the second spherical portion can be rotated and swung.
  • the holding member is provided with a housing portion having the holding hole that is elastically fitted and held.
  • the intermediate connecting portion has a larger diameter than the first and second rolling portions, and the housing portion is the second spherical surface portion.
  • a third feature is that a slit is provided that allows the diameter of one end of the holding hole to be increased when the holding hole is detached.
  • the holding member in addition to the second or the third feature, includes a plurality of the housing portions arranged at intervals in the circumferential direction corresponding to the plurality of rolling elements, and the circumferential direction thereof. And a plurality of rod-like connecting portions that integrally connect the adjacent housing portions to each other.
  • the holding member is integrally connected to a hub portion located at a center portion or a radial intermediate portion thereof, and between the hub portion and the plurality of housing portions.
  • a fifth feature is that a plurality of spoke portions are provided.
  • both the transmission grooves are grooves having a U-shaped cross section.
  • a sixth feature is that the groove is widened toward the open surface side of the groove with a small taper angle.
  • the “predetermined minute taper angle” means that the transmission groove provided in the transmission groove is formed using a molding die (for example, forging, casting, sintering, etc.), That is, it is defined as a minute angle corresponding to a draft angle set when the square groove is molded.
  • the rolling elements interposed between the wavy annular transmission grooves of the pair of transmission members that are opposed to each other with the speed change mechanism provided between them are transferred to both transmission grooves.
  • First and second rolling parts each having a first spherical part that engages movably on the outer peripheral part and fitted in both the transmission grooves, are integrally connected between the two rolling parts and both transmissions. Since the intermediate coupling part rotatably fitted and supported in the holding hole of the holding member between the members is provided, the contact angle of the rolling element with respect to each transmission groove is sufficiently ensured while ensuring a sufficient interval between the two transmission members.
  • the thrust load generated between the transmission groove and the rolling elements can be greatly reduced, the transmission efficiency of the speed change mechanism can be effectively increased, and the thrust receiving portion that faces the rear surface of the transmission member To reduce the load on the equipment and reduce the weight and durability of the equipment. It can be.
  • the holding member can be installed without difficulty between the two transmission members having a sufficient facing distance, this holding member allows the proper mutual positional relationship between the plurality of rolling elements (that is, the plurality of the two transmission grooves). The positional relationship corresponding to the intersection of the rolling elements can be easily and accurately maintained, and the assembly workability can be improved.
  • the rolling elements can mutually exert vibration suppressing action (for example, some rolling elements can Since the holding member can effectively suppress the violence of some of the rolling elements in cooperation with other rolling elements when attempting to run violently when passing through the sudden curvature change portion of the transmission groove) Smooth rolling along the transmission groove of the entire rolling element can be ensured, which can contribute to improvement of transmission efficiency.
  • the intermediate coupling portion of the rolling element has a second spherical surface portion on the outer peripheral portion, and the second spherical surface portion is fitted elastically so as to be able to rotate and swing. Since the housing part having the holding hole for holding is provided in the holding member, the housing part allows a slight inclination of the rolling element between the first and second transmission grooves, and thereby the holding member rolls. Avoiding an excessive bending load from the moving body can contribute to improving the durability of the holding member. In addition, since the housing portion elastically holds the intermediate coupling portion of the rolling elements, it is possible to eliminate backlash between the housing portion and the intermediate coupling portion of the rolling elements, and is effective in suppressing misalignment between the rolling elements.
  • the vibration suppressing effect between the rolling elements can be enhanced during transmission.
  • the holding member having a plurality of housing portions can be restricted in the axial position by the second spherical surface portion of the outer peripheral surface of the intermediate coupling portion of the rolling element, and cannot move in the axial direction during transmission. Therefore, the collision and rubbing with the transmission members on both sides can be effectively prevented, and the transmission efficiency and durability can be improved.
  • the rolling element has an intermediate connecting portion larger in diameter than the first and second rolling portions, and the cylindrical housing portion rotates the second spherical portion. Also, it has a spherical bearing surface that fits and holds in a swingable manner on the inner peripheral surface of the holding hole, and this housing part is held when the intermediate coupling part is fitted and detached from the holding hole Since a slit that allows the diameter of one end of the hole to be expanded is provided, the rolling element can be easily fitted into the housing part with a large-diameter intermediate coupling part without being obstructed by the rolling part. Further, the assembly of the holding member and the plurality of rolling elements can be easily obtained, and the elastic support for the rolling elements (intermediate connecting portion) by the housing portion can be performed accurately.
  • the holding member is provided between the plurality of housing portions arranged at intervals in the circumferential direction corresponding to the plurality of rolling elements and the housing portions adjacent to each other in the circumferential direction. Since the rod-shaped connecting portion is bent and deformed, the holding member can exhibit an appropriate elasticity, so that some of the rolling elements have a sudden change in curvature of the transmission groove. When trying to rampage when passing through, the buffering effect of the holding member itself and the vibration suppression effect due to the cooperation of the holding member and other rolling elements combine, and some rolling elements are rampant Can be suppressed.
  • the holding member includes a hub portion located at a central portion or a radial intermediate portion thereof and a plurality of spoke portions integrally connecting the hub portion and the plurality of housing portions. Therefore, the rigidity of the rod-shaped connecting portion can be supplemented by the reinforcing effect of the hub and spokes, and the overall rigidity and strength of the holding member can be effectively increased.
  • the rolling element and the housing portion are moved by the centrifugal force. Can be effectively suppressed.
  • the inner surfaces of the two transmission grooves facing each other are widened in a pre-expanded manner toward the open surface side of the groove with a predetermined minute taper angle.
  • the second rolling part) and the thrust load generated between the transmission groove can be greatly reduced, and the thrust body can be accurately positioned in the thrust direction with respect to the transmission groove. It can contribute to prevention.
  • the cross-sectional shape of each transmission groove is U-shaped, the forming accuracy of each transmission groove (and hence the accuracy of the contact angle between the transmission groove and the rolling element) can be easily increased. The load can be stabilized.
  • 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.
  • First and second rolling elements 23a, 23b,... First and second rolling parts 23m, 26m of the first rolling element, intermediate connection parts 26a, 26b of the first and second rolling elements, first and second rolling elements of the second rolling element.
  • FIGS. 1 to 8 First, an embodiment of the present invention shown in FIGS. 1 to 8 will be described.
  • a differential device D as a transmission device is housed in a transmission case 1 of an automobile together with a transmission.
  • 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.
  • 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 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).
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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
  • the hollow portion SP of the second transmission member 8 is used as a storage space for the balance weight W.
  • 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.
  • 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. .
  • 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 ⁇ .
  • the predetermined minute taper is used.
  • the angle ⁇ 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 ⁇ 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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).
  • 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.
  • 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.
  • 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.
  • a corrugated fourth transmission groove 25 centered on the first axis X1 is formed 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.
  • 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 ⁇ 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 ⁇ 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. .
  • 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.
  • 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
  • the wave number of the fourth transmission groove 25 is Z4.
  • 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.
  • 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.
  • the first and second transmission mechanisms T1 and T2 both constitute the transmission mechanism of the present invention.
  • the first transmission member 5 constitutes one transmission member
  • the second transmission member 8 constitutes the other transmission member
  • the first transmission groove 21 constitutes one transmission groove
  • the second transmission groove 22 constitutes the other transmission groove.
  • the third transmission member 9 constitutes one transmission member
  • the second transmission member 8 constitutes the other transmission member
  • the fourth transmission groove 25 serves as one transmission groove.
  • the third transmission groove 24 constitutes the other transmission groove.
  • the ring gear Cg is driven by the power from the engine, and the differential case C and therefore the first
  • 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.
  • 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.
  • the third transmission member 9 is driven with the speed increasing ratio.
  • 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.
  • the first transmission member 5 drives the eccentric rotating member 6 with a double speed increasing ratio.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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.
  • 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.
  • the contact angle ⁇ 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 °.
  • the contact angle ⁇ 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.
  • 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.
  • 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.
  • the first retainer H1 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.
  • 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.
  • 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.
  • the vibration suppressing effect between the first rolling elements 23 during transmission is obtained.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 ⁇ .
  • 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 ⁇ with the grooves 21, 22; 24, 25 is easily increased, and the above-described thrust load is stabilized.
  • 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.
  • 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.
  • 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.
  • another functional component for example, the eccentric rotating member 6
  • 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.
  • the first and second drive axles S1 and S2 drive shafts
  • the present invention can be implemented in various transmission devices other than the differential gear. is there.
  • 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.
  • a transmission (reduction gear or speed increaser) is the transmission device of the present invention.
  • the transmission may be a transmission for a vehicle or a transmission for various mechanical devices other than the vehicle.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the second transmission groove 22 may be provided, and the third transmission groove 24 may be provided on the other surface.
  • each transmission groove 21,22; 24,25 of 1st, 2nd transmission mechanism T1, T2 is made into the corrugated cyclic
  • these transmission grooves are 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.
  • the eccentric rotation member 6 and the third transmission member 9 may be directly supported by the differential case C.
  • 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.
  • 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.
  • 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.
  • the selection of the constituent material of the second retainer H2 and the rod-like connecting portion 54 are exemplified.
  • the hub portion 55 and the spoke portion 57 may be omitted from the second retainer H2.
  • the hub portion 55 ′ is formed in 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.
  • the transmission device includes two transmission mechanisms (that is, the first and second transmission mechanisms T1 and T2).
  • the present invention provides a transmission device including one or more transmission mechanisms. Is also applicable.
  • 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.
  • the first and second retainers H1, H1 ', and H2 as the holding members are made of synthetic resin.
  • materials other than the synthetic resin material for example, metal materials and ceramics are used.
  • the first and second retainers may be formed of a material or the like.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un engrenage comprenant un élément de transmission doté d'un premier axe comme axe central, et un autre élément de transmission pouvant tourner autour du premier axe tout en tournant autour d'un deuxième axe qui est décalé par rapport au premier axe. Un mécanisme de transmission entre les deux éléments de transmission comprend : une rainure de transmission présentant une forme d'onde annulaire, située sur le premier élément de transmission et centrée autour du premier axe ; une autre rainure de transmission présentant une forme d'onde annulaire, située sur l'autre élément de transmission et centrée autour du deuxième axe ; ainsi qu'une pluralité d'éléments roulants interposés dans une pluralité de parties s'entrecoupant des deux rainures de transmission. Les éléments roulants (23) comprennent chacun : des première et deuxième parties de roulement (23a 23b), chaque partie comportant une première partie de surface sphérique (r1) sur le périmètre externe qui vient en prise par roulement avec les rainures de transmission (21, 22) des éléments de transmission (5, 8) ; et une partie de liaison intermédiaire (23m) reliant solidaires les parties de roulement et venant en prise par rotation avec un trou de retenue (31) d'un élément de retenue (H1), soutenue par celui-ci. Cette configuration permet de maintenir à zéro ou de réduire de façon appropriée la poussée axiale entre les rainures de transmission et les éléments roulants pendant la transmission, ce qui permet d'assurer des espaces de montage pour les éléments de retenue entre les deux éléments de transmission.
PCT/JP2017/012722 2016-03-29 2017-03-28 Engrenage WO2017170588A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-065365 2016-03-29
JP2016065365A JP2017180557A (ja) 2016-03-29 2016-03-29 伝動装置

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WO2017170588A1 true WO2017170588A1 (fr) 2017-10-05

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019212001A1 (fr) * 2018-05-02 2019-11-07 株式会社エンプラス Réducteur

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109973613B (zh) * 2019-03-28 2020-06-23 燕山大学 链轮激波推杆活齿二级减速器

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2700310A (en) * 1951-11-13 1955-01-25 Carl H Viebrock Power transmitting device
JPH0124417B2 (fr) * 1982-09-30 1989-05-11 Phillips Petroleum Co
JP2016035325A (ja) * 2014-07-31 2016-03-17 日本精工株式会社 アクチュエータ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2700310A (en) * 1951-11-13 1955-01-25 Carl H Viebrock Power transmitting device
JPH0124417B2 (fr) * 1982-09-30 1989-05-11 Phillips Petroleum Co
JP2016035325A (ja) * 2014-07-31 2016-03-17 日本精工株式会社 アクチュエータ

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019212001A1 (fr) * 2018-05-02 2019-11-07 株式会社エンプラス Réducteur

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