Classifications

• • 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
  • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
  • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
  • F16H15/04—Gearings providing a continuous range of gear ratios
  • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
  • F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
  • F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
  • F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces

Definitions

• a toroidal continuously variable transmission for a four-wheel drive vehicle according to the present invention is used as a transmission unit constituting an automatic transmission device for a four-wheel drive vehicle.
• Toroidal-type continuously variable transmissions have been studied as transmissions for automobiles, and are being implemented in part.
• Automatic transmissions for four-wheel drive vehicles incorporating large-sized engines that generate large torque for passenger cars A structure suitable as a transmission unit of the apparatus is described in, for example, Patent Document 1 and is conventionally known.
• 3 to 6 show a toroidal-type continuously variable transmission for a four-wheel drive vehicle having a large displacement described in Patent Document 1.
• This toroidal type continuously variable transmission 1 for a four-wheel drive vehicle includes three first power rollers 4 and 4 between a first input side disk 2 and a first output side disk 3, and a second input side disk.
• Three second power rollers 7 are provided between 5 and the second output side disk 6, respectively, and the power can be transmitted by a total of six power rollers 4 and 7.
• a forward / reverse switching unit 10 for switching between forward and backward movement is provided in series between the front half portion 9a and the rear half portion 9b in the power transmission direction.
• This forward / reverse switching unit 10 which is a planetary gear mechanism, switches between a forward state and a reverse state by selecting and connecting a forward clutch 11 and a reverse clutch 12, each of which is a wet multi-plate clutch. .
• the rearward / reverse switching unit 10 as described above A toroidal continuously variable transmission 1 for four-wheel drive vehicles is provided. Then, the input portion of the toroidal type continuously variable transmission 1 for a four-wheel drive vehicle, that is, the portion connected to the output portion of the forward / reverse switching unit 10 and the output portion, that is, the front wheel drive shaft 13 and the rear wheel The speed ratio with the portion connected to the drive shaft 14 is continuously changed.
• This toroidal continuously variable transmission 1 for a four-wheel drive vehicle is provided around the latter half 9b.
• the first and second input side disks 2 and 5 are arranged in the vicinity of both front and rear end portions of the rear half portion 9b so that the inner side surfaces, which are concave surfaces each having an arcuate cross section, face each other and are concentric with each other. It is supported so that it can rotate in synchronization with each other.
• the first input side disk 2 provided on the front side (left side in FIG. 3) is spline-engaged with the base end portion of the carrier 15 constituting the forward / reverse switching unit 10 and moved forward. Is preventing movement.
• the second input side disk 5 provided on the rear side (right side in FIG. 3) is supported via a ball spline 16 at the rear end portion of the latter half portion 9b. Then, the second input disk 5 is directed toward the first input disk 2 by the hydraulic loading device 17 so that it can be pressed.
• a support cylinder 18 is provided concentrically with the latter half portion 9b around the middle portion of the latter half portion 9b.
• the support cylinder 18 is supported and fixed at both ends by the inner diameter side ends of the stays 19 and 19.
• These stays 19 and 19 support and fix their outer diameter side ends to support rings 20 and 20 described later, respectively, and first and second swing frames 21 and 22 described later also swing themselves.
• the first and second support frames 23 and 24 are configured to support each other.
• the latter half 9b is supported inside the support cylinder 18, and the first and second output side disks 3 and 6 are supported around the support cylinder 18 so as to be freely rotatable and axially displaceable. Yes.
• These output side disks 3 and 6 are capable of relative rotation while supporting an axial load (thrust load) applied between them by a thrust-dollar bearing 25 provided therebetween.
• a front wheel output gear 26 is fixed to the outer surface side of the first output side disk 3, and the front wheel output gear 26 and the front wheel drive shaft 13 are connected via a front wheel driven gear 27.
• the front output shaft 13 can be driven to rotate by the first output side disk 3.
• the rotation of the front wheel drive shaft 13 can be transmitted to a front wheel (not shown) via a front wheel differential gear 28.
• a rear wheel output gear 29 is fixed to the outer surface side of the second output side disk 6, and the rear wheel output gear 29 and the rear wheel drive shaft 14 are connected to each other.
• the second wheel 6 is coupled via a rear wheel driven gear 30 so that the rear wheel drive shaft 14 can be driven to rotate by the second output side disk 6.
• the rotation of the rear wheel drive shaft 14 can be transmitted to the rear wheels via a rear wheel differential gear (not shown).
• the three first power rollers 4, 4 are provided between the inner side surface of the first input side disc 2 and the inner side surface of the first output side disc 3, and the second input side disc.
• the three second power rollers 7 are sandwiched between the inner surface of 5 and the inner surface of the second output side disk 6.
• the first and second power rollers 4 and 7 are respectively provided on the inner surfaces of the first and second trolleys 31 and 32, and the displacement shafts 33 and 33 provided in a state where the inner surface force protrudes. It is supported so that it can rotate freely.
• the centers of the displacement shafts 33 and 33 and the centers of the power rollers 4 and 7 are shifted from each other in a direction substantially perpendicular to the axial directions of the disks 2, 5, 3, and 6 ( Offset).
• Each of these first and second troons 31 and 32 swings around the first and second pivots 34 and 34 (the second pivot is not shown) concentrically arranged at both ends of each. To do. These pivots 34 and 34 do not intersect the central axis of each of the disks 2, 5, 3, and 6, but are perpendicular or perpendicular to the direction of the central axis of each of the disks 2, 5, 3, and 6. It exists at the position of twist in the direction close to.
• the first and second troons 31 and 32 are supported on both end portions of the first and second swing frames 21 and 22 so as to be swingably displaceable.
• the disk 2, 5, 3, 6 is supported so as to be swingable and displaceable about a support shaft 35, 35 provided in a direction parallel or nearly parallel to the central axis of the disk 2, 5, 3, 6.
• Each of the first and second support frames 23 and 24 has a pair of support rings 20 and 20 arranged in parallel to each other, outside the three support portions 36 and 36 constituting the stay 19. They are connected to each other through the radial end.
• the support shafts 35 and 35 constitute the first and second support frames 23 and 24 at intermediate positions of the support portions 36 and 36 with respect to the circumferential direction of the support rings 20 and 20, respectively.
• a pair of support rings 20 and 20 are spanned between each other. Therefore, the first and second swing frames 21, 22 are It is supported in a freely swingable manner between the struts 36 adjacent to each other in the circumferential direction.
• the control valve 40 for controlling the supply and discharge of the pressure oil to and from the hydraulic cylinders 37a and 37b is supported by the support rings 20 and 20, respectively.
• the cam surface 41 provided on the outer surface of the ON 31 and 32 displaces the spool 43 of the control valve 40 via the plunger 42 attached to the control valve 40 to switch the control valve 40.
• the sleeve 44 constituting the control valve 40 together with the spool 43 is displaced to a predetermined position by the control motor 45 so that a desired gear ratio can be realized at the time of shifting.
• Such a control valve 40 and a control motor 45 are provided on the first cavity 46 side including the first input side disk 2 and the first output side disk 3, and on the second input side disk 5 and the second output disk 5.
• the control valve 45 on the first cavity 46 side is controlled by the control motor 45 on the first cavity 46 side
• the control valve 40 on the second cavity 47 side is controlled by the control motor 45 on the second cavity 47 side.
• 40 are controlled in synchronization with each other (in a straight traveling state) or independently of each other (in a turning state) based on a command signal of a controller force (not shown) having a microcomputer built therein.
• the first and second swing frames 21 and 22 are connected to the support shafts 35 on the basis of the supply and discharge of the pressure oil to and from the hydraulic cylinders 37a and 37b. , 35 is swung and displaced in a predetermined direction by a predetermined amount.
• the first and second troons 31 and 32 supported by the swing frames 21 and 22 perform an arc motion (swivel motion) around the support shafts 35 and 35, respectively.
• Patent Document 2 Conventionally, a structure described in Patent Document 2 is known as a structure for supporting an output-side disk in a state where it can be rotated by a pair of steps and positioned in an axial direction.
• the structure described in Patent Document 2 is not intended for a four-wheel drive vehicle, but is intended for a single output side disk, it is a toroidal for a four-wheel drive vehicle. It cannot be applied to a type continuously variable transmission.
• a thrust angular ball bearing force that supports the output side disk has a pair of race rings independent of the output side disk, so that installation space increases.
• Patent Document 1 Japanese Patent Laid-Open No. 2001-165262
• Patent Document 2 Japanese Patent Laid-Open No. 2003-314645
• the toroidal type continuously variable transmission for a four-wheel drive vehicle according to the present invention is an axial direction of the first and second output side discs that ensures efficiency and durability in view of the above-described circumstances. It was invented to realize a practical structure that can regulate the position.
• the toroidal type continuously variable transmission for a four-wheel drive vehicle of the present invention is similar to the toroidal type continuously variable transmission for a four-wheel drive vehicle described in the above-mentioned Patent Document 1 and the like and also known in the art.
• the gear ratio between the input part and the output part housed in this housing is continuously changed.
• the toroidal-type continuously variable transmission unit includes the first and second input disks, the first output disk, the second output disk, and four or more even first pivots.
• a plurality of first trunnions, a plurality of first displacement shafts, a plurality of first power rollers, an even number of four or more second pivots, a plurality of second trunnions, and a plurality of second displacements A shaft and a plurality of second part rollers are provided.
• both the first and second discs are rotatably supported concentrically and in synchronism with each other in a state where the inner side surfaces, which are concave surfaces each having an arcuate cross section, face each other.
• the first output side disk has a concave surface with a circular arc cross section, and the first and second input side disks are in a state where the inner side surface is opposed to the inner side surface of the first input side disk.
• the first and second input side disks are concentrically and rotatably supported independently.
• the second output-side disk is concentric with the first output-side disk in a state where the inner surface, which is a concave surface having an arcuate cross section, faces the inner surface of the second input-side disk, and
• the first output side disk and the first and second input side disks are rotatably supported independently of each other.
• Each of the first pivots is a portion between the first input side disk and the first output side disk, and exists at a twisted position with respect to the central axis of each of the disks.
• Each of the first displacement shafts protrudes from an inner surface of each of the first trunnions.
• Each of the first power rollers is supported between the inner side surface of the first input side disk and the inner side surface of the first output side disk in a state of being rotatably supported around the first displacement shaft. These are sandwiched between them, and each peripheral surface is a spherical convex surface.
• Each of the second pivots is a portion between the second input side disk and the second output side disk, and exists at a twisted position with respect to the central axis of each of the disks.
• Each of the second trunnions swings about each of the second pivots.
• each of the second displacement shafts protrudes from the inner surface force of each of the second trillions.
• each of the second power rollers is rotatably supported around each of the second displacement shafts, and the inner surface of the second input disk and the inner surface of the second output disk.
• Each peripheral surface is a spherical convex surface.
• the front wheel drive shaft can be driven to rotate by the first output disk, and the rear wheel drive shaft can be driven to rotate by the second output disk.
• the first and second output side disks are provided at positions sandwiching the both output side disks from both axial sides.
• Positioning in the axial direction is achieved by a pair of thrust ball bearings.
• one of the pair of raceway grooves constituting each of the thrust ball bearings is formed on the inner diameter side end of the inner side surface of each of the output side disks. It is formed directly on the disc.
• both the output side discs are positioned in the axial direction.
• the positional relationship of the constituent members can be matched between the first and second cavities.
• both the thrust ball bearings are configured to include the raceway grooves formed directly on the two output side disks, the thrust ball bearings can be configured in a small size, and the installation space is increased, and the mounting force is also assembled. Work can be done easily.
• FIG. 1 is a cross-sectional view of a main part showing an embodiment of the present invention.
• FIG. 2 is an enlarged view of part A in FIG. [3] Cross-sectional view showing an example of a conventional structure.
• FIG. 4 BB sectional view of Fig. 3.
• FIG. 6 A cross-sectional view showing a portion substantially the same as FIG. 5 cut along a plane including the central axis of the first pivot provided at both ends of the first trillion.
• both the first and second input-side disks are supported around the input shaft and spaced apart in the axial direction.
• the first and second output side disks are supported around the input shaft via a cylindrical support cylinder.
• a pair of outward flange-shaped flanges are formed in the vicinity of both ends of the outer peripheral surface of the support cylinder.
• the other raceway groove of each pair of raceway grooves constituting a pair of thrust ball bearings is directly attached to the side surface of the both flanges or a separate raceway ring from the flanges. Form on the side.
• both the output side discs are sandwiched from both axial sides by the both thrust ball bearings, and both the output side discs are rotatably supported with the axial position regulated inside the housing. Assembling work can be easily performed.
• a thrust-dollar bearing is provided between the first and second output-side disks, and both these outputs are provided.
• the side disks are allowed to rotate relative to each other while supporting the thrust load applied between them.
• the transmission of power between the first output side disk and the front wheel drive shaft and the transmission of power between the second output side disk and the rear wheel drive shaft are respectively performed by helical gears.
• the direction of the thrust load generated at the joint portion of the structure is the direction in which the two output side disks are pressed toward the thrust needle bearing.
• Figures 1-2 show an embodiment of the invention.
• the feature of the present invention is that it prevents the poor synchronization of the transmission ratio and the instability of the transmission ratio control and ensures sufficient durability.
• First and second output side disks 3, 6 This is to realize a compact and easy-to-assemble structure that supports the input shaft 9 around the rear half 9b of the input shaft 9 while being positioned in the axial direction. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 3 to 6 described above, overlapping illustrations and explanations are omitted or simplified. The explanation will focus on the strong parts.
• both of these are placed inside the housing (not shown).
• the input side disks 2 and 5 are rotatably supported in synchronization with each other.
• a support cylinder 18a is supported around the portion between the two input side disks 2 and 5 at the intermediate portion of the latter half portion 9b.
• the support cylinder 18a is composed of a pair of support cylinder elements 49 and 49 divided into two in the axial direction, and flange portions 50 and 50 having outward flange shapes are formed in the vicinity of both end portions of the outer peripheral surface, respectively.
• both end portions projecting from both flange portions 50 and 50 are directly or directly connected to the support ring portions 51 and 51 provided at the center portions of the stages 19 and 19, respectively. It supports in the state which aimed at positioning in the direction of an axis via.
• a sleeve 53 is externally fitted with an interference fit at the abutting side end portions of the both support cylinder elements 49, 49 to ensure the bending rigidity of the support cylinder 18a.
• the latter half 9b is rotatably supported by a pair of inner diameter side radial-single bearings 48, 48 inside the support cylinder 18a.
• the first and second output side disks 3, around the support cylinder 18a, spanned between the support ring portions 51, 51 of the pair of stays 19, 19. 6 is rotatably supported by the outer diameter side radial-one dollar bearings 54 and 54, respectively.
• the first, The second output side disks 3 and 6 are abutted via a thrust / single dollar bearing 25, and are capable of relative rotation while supporting an axial load (thrust load) applied between them.
• the thrust-dollar bearing 25 regulates the positional relationship between the output side disks 3 and 6 with respect to the axial direction.
• the positional relationship in the axial direction of the two output side disks 3 and 6 with respect to the two stages 19 and 19 is expressed by the inner diameter of the inner surface of the first and second output side disks 3 and 6.
• This is achieved by a pair of thrust ball bearings 55 and 55 provided between the side end portion and the both flange portions 50 and 50.
• One of the pair of raceway grooves 56a and 56b (Fig. 2) constituting the thrust ball bearings 55 and 55, respectively, is formed in each of the output side disks 3 and 6, respectively. It is formed directly on the inner diameter side end of the side surface for these output side disks 3 and 6.
• the other raceway groove 56b, 56b of the pair of raceway grooves 56a, 56b is directly on the side surface of the both side parts 50, 50 (the structure on the right side in FIGS. It is formed on the side surface (the left-side structure in FIGS.
• the race 57 has a balance with the thickness of the spacer 52, so that the output side disks 3 and 6 are not rattled between the stages 19 and 19 (displaced in the axial direction).
• a plurality of types having different thickness dimensions are prepared as one or both of the raceway ring 57 and the spacer 52, and those having an appropriate thickness dimension are selectively used.
• the front output gear 26 fixed to the outer surface of the first output disk 3 and the front wheel driven gear 27 fixed to the front drive shaft 13 are screwed together, and the second output disk A rear wheel output gear 29 fixed on the outer surface side of 6 and a rear wheel drive gear 30 fixed to the rear wheel drive shaft 14 are combined.
• These gears 26, 27, 29, and 30 are all helical gears for the purpose of reducing vibrations and noise generated at the joints.
• the direction of the thrust load generated at the meshing part (meshing part of the gear transmission mechanism) between the gears 26, 27, 29, and 30 during forward travel is determined according to the direction of the thrust load.
• the direction of pressing toward the dollar bearings 25 so as to be close to each other in other words, the direction not facing the thrust ball bearings 55 and 55 described above.
• the thrust ball bearings 55, 55 are configured to include the race grooves 56a, 56a formed directly on the output side disks 3, 6, so that the configuration can be reduced in size and installation space can be reduced. The assembly work can be done easily.
• the thrust ball bearings 55 and 55 are formed directly on the output side disks 3 and 6 of the pair of raceway grooves 56a and 56b.
• the other raceway grooves 56b, 56b other than one raceway groove 56a, 56a are formed directly on the side surfaces of the both flange portions 50, 50 formed on the outer peripheral surface of the support cylinder 18a or separately from the flange portion 50. It is formed on the side surface of the race ring 57. For this reason, both the output side discs 3 and 6 are sandwiched from both axial sides by the thrust ball bearings 55 and 55, and the output side discs 3 and 6 are rotated with the axial position regulated inside the housing. The assembly work to support freely can be easily performed.
• the direction of the thrust load generated at the meshing portion of the gears 26, 27, 29, 30 is set, and the output side disks 3, 6 are connected to the thrust-dollar bearing.
• the direction is to push toward 25.
• the thrust-dollar bearing 25 is subjected to a relatively large thrust load.
• the load capacity of the thrust-dollar bearing 25 is larger than that of both thrust-dollar bearings 55, 55. Much bigger.
• La 59 and 59 are installed.
• This synchronization cable is spanned between a plurality of troons 31 (or 32) existing in the same cavity 46 (or 47), and a plurality of trolons 31 (or 32) are connected to each other. The amount of movement is mechanically matched. Since such a synchronous cable structure is well known in the technical field of toroidal-type continuously variable transmissions, detailed illustration and description thereof will be omitted.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Friction Gearing (AREA)
• Rolling Contact Bearings (AREA)
• Gear Transmission (AREA)

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• 2004
  • 2004-06-30 JP JP2004192641A patent/JP4622342B2/ja not_active Expired - Fee Related
• 2005
  • 2005-06-28 DE DE112005001576T patent/DE112005001576T5/de not_active Withdrawn
  • 2005-06-28 WO PCT/JP2005/011832 patent/WO2006003887A1/ja active Application Filing

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