JP4550924B2 - Multi-speed transmission - Google Patents

Description

  The present invention relates to a multi-stage transmission which is applied to a vehicle transmission or the like and includes a frictional conduction mechanism of a type in which a drive transmission portion is brought into contact by utilizing elastic deformation of a thin disk-shaped disk.

  2. Description of the Related Art Conventionally, as a transmission using a disk, a so-called Bayer transmission having a frictional conduction mechanism including a plurality of cone disks and a plurality of flange disks is known (for example, FIG. 3 and FIG. (See Fig. 4).

  In this Bayer transmission, the power input to the input shaft is transmitted to a large number of spline shafts via gears, and further distributed evenly to a plurality of cone disk groups. The cone disk group is alternately arranged between a plurality of flange disk groups arranged at the center, and is pressed by a pressing force of a spring and a face cam. Further, the cone disk group is arranged at three positions on the outer periphery of the flange disk group, provided with a shift operation link mechanism, and performs a shift operation by moving the cone disk group into and out of the flange disk group.

The power from the input shaft is transmitted from the cone disk group to the flange disk group through the oil film, and is transmitted to the output shaft through the face cam. At this time, the closer the contact point of the flange disk group is to the center of the cone disk group, the lower the output shaft becomes, and the closer the contact point of the flange disk group is to the outer periphery of the cone disk group, the faster the output shaft.
3 and 4 of Japanese Utility Model Laid-Open No. 3-2954

  However, the conventional Bayer transmission has a structure in which the cone disk group is sandwiched by the flange portion formed on the outer peripheral portion of the flange disk group disposed in the center, and the flange drive radius on the output side is set as the fixed diameter. It has been decided. For this reason, the flange drive radius of the output side flange disk group is larger than the variable drive radius of the input side cone disk group, and only a reduction-side speed ratio of 1 or less is obtained as the speed ratio. That is, there is a problem that the range of the speed ratio that can be set becomes narrow. For example, when there is a request for the speed increasing side gear ratio, this demand cannot be met.

  Further, in order to stably operate without sticking, the cone disk groups are arranged at three positions on the outer periphery of the flange disk group arranged at the center, and the three cone disk groups are held by the movable shaft and adjacent to each other. A configuration is adopted in which a speed change operation link mechanism is arranged at a spatial position of the cone disk group. This increases the weight of the tapered cone disk group that becomes thicker on the shaft side, and the structure is complex, the number of parts is large, and movable space is required. There was a problem that could not be achieved.

  Furthermore, the contact structure of the torque transmission contact portion is a circumferential contact structure with a protrusion and a flat surface sandwiching the flat cone disk group at the flange portion formed on the outer peripheral portion of the flange disk group disposed in the center. An ellipse or ellipse with a long direction driving radius is formed. Therefore, in the contact area of the torque transmission contact portion that is enlarged in the circumferential direction, relative rotation around the torque transmission contact center point occurs, and there is a problem that spin loss of the transmission torque increases. there were.

  The present invention has been made by paying attention to the above-described problems, and achieves a gear shifting function having a high degree of freedom in setting a gear ratio, including a speed increasing ratio, while achieving low cost, light weight, and compactness, and torque transmission / It is an object of the present invention to provide a multi-stage transmission that can exhibit a clutch function for switching off and can reduce spin loss of transmission torque at each gear ratio position.

In order to achieve the above object, in the multi-stage transmission of the present invention,
An input shaft connected to the prime mover and supported by the transmission case member;
An output shaft disposed in parallel to the input shaft and supported by a transmission case member;
A disc-shaped input disk provided on the input shaft and having an outer peripheral end disposed close to the output shaft;
A disc-shaped output disk provided on the output shaft and having an outer peripheral end disposed close to the input shaft;
Of the disk overlap region where the input disk and the output disk overlap each other, the input disk and the output disk are provided so as to be movable along an axis connection line connecting the axis of the input shaft and the axis of the output shaft. A pair of pressing means that sandwich and press both discs at a position and form a torque transmission contact portion by elastic deformation of both discs,
The input disk has a plurality of input side protrusions formed concentrically at different radii from the axis of the input shaft on the disk surface;
The output disk has a plurality of output-side protrusions formed concentrically at different radii from the axis of the output shaft on the disk surface;
The plurality of input-side ridges and the plurality of output-side ridges are set such that the length of the shaft connection line is divided into an input-side drive radius and an output-side drive radius according to a plurality of required speed ratios, The tops of both protrusions are arranged opposite to each other on the shaft connecting line.

Therefore, in the multi-stage transmission of the present invention, when both disks are sandwiched and pressed by a pair of pressing means, a torque transmission contact portion is formed by elastic deformation. If this torque transmission contact portion is formed at an intermediate position on the shaft connection line, the input side drive radius from the axis of the input side contact circle is the same as the output side drive radius from the axis of the output side contact circle, A constant speed ratio is obtained between the input shaft and the output shaft. If the torque transmission contact part is formed at a position moved from the constant speed ratio position to the input shaft side, the input side drive radius is shortened, the output side drive radius is lengthened, and the speed is reduced between the input shaft and the output shaft. Ratio (low side transmission ratio) is obtained. On the other hand, if the torque transmission contact portion is formed at a position moved from the constant speed ratio position to the output shaft side, the input side drive radius becomes longer, the output side drive radius becomes shorter, and between the input shaft and the output shaft, The speed increasing ratio (high side gear ratio) is obtained.
When the pressing force for holding and pressing both disks by the pressing means is released, torque transmission from the input shaft to the output shaft is interrupted.
Further, the plurality of input side ridges included in the input disk and the plurality of output side ridges included in the output disk have an input side driving radius and an output side driving radius according to a plurality of required transmission gear ratios. The tops of the two ridges are arranged opposite to each other on the axial connection line. That is, since it is a contact structure by protrusions, the contact shape of the torque transmission contact portion is small and round, and the contact area is also small. Accordingly, the twisting pressure contact generated by relative rotation around the torque transmission contact center point is suppressed, and the spin loss of the transmission torque is reduced.
As a result, it has a simpler structure and fewer parts compared to conventional Bayer transmissions, while achieving cost reduction, weight reduction, and compactness, while having a high gear ratio setting freedom including speed ratio In addition, the clutch function for switching between torque transmission / interruption can be exhibited together, and the spin loss of the transmission torque can be reduced at each gear ratio position.

  Hereinafter, the best mode for realizing the multi-stage transmission of the present invention will be described based on a first embodiment shown in the drawings.

First, the configuration will be described.
FIG. 1 is an overall schematic diagram showing a vehicular automatic transmission system to which a multi-disc multi-stage transmission unit T / U (an example of a multi-stage transmission) according to a first embodiment is applied.

  As shown in FIG. 1, an automatic transmission system for a vehicle to which a multi-disc multi-stage transmission unit T / U of Embodiment 1 is applied includes an engine 1 (prime mover), a transmission case 2, an input shaft 3, and a multi-disc. Multi-speed transmission unit T / U, output shaft 4, reverse gear 5, reverse idler gear 6, output gear 7, synchro mechanism 8, final gear 9, differential gear unit 10, and left and right drive shafts 11 , 12 and left and right drive wheels 13, 14.

  The multi-disc multi-stage transmission unit T / U includes a primary disk group 150 constituted by a plurality of input disks 15, a secondary disk group 160 constituted by a plurality of output disks 16, and a pair of pressing means as pressing means. Rollers 17, 17, input shaft support frames 18, 18 that support the input shaft 3, and output shaft support frames 19, 19 that support the output shaft 4 are provided.

  That is, the vehicular automatic transmission system to which the multi-disc multi-stage transmission unit T / U of the first embodiment is applied has a three-axis configuration including the input shaft 3, the output shaft 4, and the left and right drive shafts 11 and 12. In addition, when the D range (drive range) is selected, the multi-disc multi-speed transmission unit T / U achieves forward traveling at 7-speed automatic transmission, and when the R range (reverse range) is selected, the synchronization mechanism 8 is synchronized. 1st reverse running is achieved by meshing.

  FIG. 2 is an overall perspective view showing the multi-disc multi-stage transmission unit T / U according to the first embodiment. 3 is a cross-sectional view of the multi-disk multi-stage transmission unit T / U according to the first embodiment taken along line AA in FIG. Hereinafter, the overall configuration of the multi-disc multi-stage transmission unit T / U will be described.

  As shown in FIG. 2, the multi-disc multi-stage transmission unit T / U according to the first embodiment includes an input shaft 3, an output shaft 4, a primary disk group 150 composed of a plurality of input disks 15, and a plurality of sheets. Secondary disk group 160 constituted by the output disk 16, a pair of pressing rollers 17, 17 (pressing means), input shaft support frames 18, 18 (transmission case member), and output shaft support frames 19, 19 (shift) Machine case member) and a roller rotating shaft 20.

  The input shaft 3 is connected to the engine 1 and is rotatably supported at both ends by input shaft support frames 18 and 18. As shown in FIGS. 2 and 3, the input shaft 3 is configured by arranging a plurality of disk-shaped input disks 15 whose outer peripheral ends are arranged close to the output shaft 4 at equal intervals in the axial direction. A primary disk group 150.

  The output shaft 4 is arranged in parallel to the input shaft 3 and is supported at both ends by output shaft support frames 19 and 19 so as to be rotatable. As shown in FIGS. 2 and 3, the output shaft 4 is configured by arranging a plurality of disk-shaped output disks 16 whose outer peripheral ends are arranged close to the input shaft 3 at equal intervals in the axial direction. Secondary disk group 160.

The pair of pressing rollers 17 and 17 are arranged so that the output disk 16 is inserted and disposed in each of the adjacent axial gaps of the plurality of input disks 15 so that the primary disk group 150 and the secondary disk group 160 overlap each other. Form. Then, among the disk overlapping area, movably disposed along the axis connecting line CL connecting the axis axis O ₄ of the O ₃ and the output shaft 4 of the input shaft 3, in accordance with the required gear ratio position The two disk groups 150 and 160 are sandwiched and pressed from both side positions to form a torque transmission contact portion by elastic deformation of the two disk groups 150 and 160.

  The pair of pressing rollers 17 and 17 rolls according to the rotation of both the disk groups 150 and 160 while sandwiching and pressing the primary disk group 150 and the secondary disk group 160. When the pair of pressing rollers 17 and 17 are fixed in position without any change in the required speed ratio (gear), the pair of pressing rollers 17 and 17 maintain a roller rotation axis parallel to the axis connection line CL, and the required speed ratio (gear). When the position is moved by the change, the attachment is allowed to allow the roller rotation axis to be slightly tilted according to the moving direction along the axis connection line CL. That is, as shown in FIG. 3, the pressing roller 17 supports the roller rotating shaft 20 that rotatably supports the pair of pressing rollers 17 and 17 while leaving a minute gap (backlash) intentionally.

The input disc 15, as shown in FIG. 3, the input shaft 3 to the disk surface the axis O ₃ of concentrically formed different radii by a plurality of input-side protrusion 15a, 15b, 15c, 15d, 15e , 15f, 15g. The output disk 16, as shown in FIG. 3, a plurality of output-side ridges 16a due to the different radii which are formed concentrically from the axis O ₄ of the output shaft 4 on the disk surface, 16b, 16c, 16d, 16e, 16f, 16g. Each of the radii of the input-side ridges 15a, 15b, 15c, 15d, 15e, 15f, and 15g and each of the radii of the output-side ridges 16a, 16b, 16c, 16d, 16e, 16f, and 16g has a plurality of required speed changes. According to the ratio, the length of the shaft center connection line CL is set to be distributed between the input side radius and the output side radius.

  As shown in FIG. 3, the pair of pressing rollers 17, 17 includes the input side protrusions 15 a, 15 b, 15 c, 15 d, 15 e, 15 f, 15 g, and the output in which a minute gap is maintained when the holding pressing force is released. The tops of the side ridges 16a, 16b, 16c, 16d, 16e, 16f, and 16g are clamped according to the required stepped gear ratio from the first gear (low speed) to the seventh gear (high speed). Press. Note that the first gear is achieved by a combination of the input / output ridges 15a and 16g. The second gear is achieved by a combination of the input / output ridges 15b and 16f. The third speed is achieved by a combination of the input / output ridges 15c and 16e. The fourth speed stage is achieved by a combination of the input / output side protrusions 15d and 16d. The fifth gear is achieved by a combination of the input / output ridges 15e and 16c. The sixth speed stage (OD stage) is achieved by the combination of the input / output side protrusions 15f and 16b. The seventh speed stage (super OD stage) is achieved by a combination of the input / output side ridges 15g and 16a.

The pair of pressing rollers 17, 17 are rotatably supported by a moving frame 21 that can move in a direction that coincides with the axial connection line CL, and are made by a disc spring 22 (biasing means) set on the moving frame 21. The urging force is defined as the clamping pressing force on the torque transmission contact portion.
That is, as shown in FIG. 2, the moving frame 21 surrounds the outer periphery of the disk group overlapping region where the primary disk group 150 and the secondary disk group 160 overlap each other, and is arranged so as to be movable in a direction that coincides with the axial connection line CL. is doing. And a pair of roller rotating shafts 20 and 20 parallel to the axial connection line CL are supported on a pair of roller holding frame portions 21a and 21a facing the disk surface in the moving frame 21. Further, in the moving frame 20, the pair of connecting frame portions 21 b and 21 b that connect the pair of roller holding frame portions 21 a and 21 a at both end positions in a direction of narrowing the interval between the pair of roller holding frame portions 21 a and 21 a. A disc spring 22 for providing an urging force is provided.

The moving frame 21 is provided so as to be movable in the direction of the axis connecting line CL using a screw screw 24 rotated by a stepping motor 23 (motor actuator).
That is, the first screw screw support structure 25 is provided on the input shaft support frame 18 that supports the input shaft 3, the second screw screw support structure 26 is provided on the output shaft support frame 19 that supports the output shaft 4, and the roller holding frame portion A ball screw structure 27 is provided at 21a. The screw screw 24 is supported across the first screw screw support structure 25, the second screw screw support structure 26, and the ball screw structure 27, and a stepping motor 23 is provided at the end of the screw screw 24.

The urging force adjusting means by the pair of pressing rollers 17, 17 follows the templates 28, 28 having cam surfaces 28 a, 28 a for adjusting the urging force Fd by the disc spring 22, and the surface shapes of the cam surfaces 28 a, 28 a. And moving cam followers 29 and 29.
That is, a pair of the templates 28 and 28 are arranged at both end positions of the moving frame 21 by setting that the biasing force Fs by the coil springs 30 and 30 acts in a direction to separate them from each other. The cam followers 29, 29 are provided at end positions of the pair of roller holding frame portions 21a, 21a, and the biasing force Fd by the disc spring 22 is applied to the contact surfaces of the pair of templates 28, 28 with the cam surfaces 28a, 28a. It is set to work. The biasing force F applied to the pair of pressing rollers 17, 17 (the biasing force difference (Fd−Fs) between the biasing force Fd by the disc spring 22 and the biasing force Fs by the coil spring 30) is converted into a cam of the pair of templates 28, 28. Adjustment is made by setting the surface shapes of the surfaces 28a, 28a.

  FIG. 4 is an enlarged cross-sectional view of a portion B in FIG. 3 showing a structure for holding the end portion spacing of the input / output disc of the multi-disc multi-stage transmission unit of the first embodiment. FIG. 5 is an enlarged cross-sectional view of a portion C in FIG. 3 showing the detailed structure of the input / output disk of the multi-disk multi-stage transmission unit of the first embodiment. Hereinafter, the configuration of the input / output disks 15 and 16 of the multi-disc multi-stage transmission unit T / U will be described.

The primary disk group 150 and the secondary disk group 160 are arranged such that the gaps between the end portions of the input disk 15 and the output disk 16 adjacent to each other in the axial direction are at regular intervals at the outer peripheral position of the input shaft 3 and the outer peripheral position of the output shaft 4. It has an end interval holding structure to keep.
That is, as shown in FIG. 4, the end gap holding structure at the outer peripheral portion of the input shaft 3 has the collar 31 in the disk base space formed by the input shaft 3 and the adjacent input disks 15 and 15, respectively. By arranging, a plurality of input disks 15, 15 are arranged at equal intervals. Then, by using a tightening nut 32 screwed to the input shaft 3 and a stopper projection 3a formed on the input shaft 3, the tightening nut 32 is tightened from one end side, so that a plurality of input disks 15 and 15 are equally spaced. It is clamped and fixed to the input shaft 3 while maintaining the same.
In addition, a pair of balls 33 and 33 held by a cage are arranged at the outer peripheral position of the collar 31, and the outer peripheral ends of the plurality of output disks 16 and 16 are arranged by the pair of balls 33 and 33. I keep it at intervals. The same applies to the end interval holding structure at the outer peripheral portion of the output shaft 4 (see FIG. 3).

The plurality of input side protrusions 15a, 15b, 15c, 15d, 15e, 15f, 15g and the output side protrusions 16a, 16b, 16c, 16d, 16e, 16f, 16g are input side protrusions on the input shaft 3 side. 15a and the height of the output-side ridge 16a on the output shaft 4 side are set to be the highest, and the height of the ridge is gradually decreased toward the outer peripheral side (see FIG. 3).
That is, in combination with the end interval holding structure, when the holding pressing force to the disk by the pair of pressing rollers 17 and 17 is released, the opposing input / output side ridges 15a and 16g, the input / output side ridges are opposed. 15b, 16f, I / O side ridges 15c, 16e, I / O side ridges 15d, 16d, I / O side ridges 15e, 16c, I / O side ridges 15f, 16b, gaps between I / O side ridges 15g, 16a Is secured.

  The plurality of input side ridges 15a, 15b, 15c, 15d, 15e, 15f, 15g and the output side ridges 16a, 16b, 16c, 16d, 16e, 16f, 16g have triangular cross sections as shown in FIG. The top portions 15 'and 16' of the shape are inclined top shapes having a downward inclination angle in the axial direction, and the opposing inclined top shapes are pressed with a contact angle θ.

  As shown in FIG. 5, the input disk 15 is provided with two plates each having an input-side protrusion 15e having a triangular cross section on one surface of both surfaces of the disk, and the other disk of the two plates. The surfaces are configured by bonding the input side protrusions 15e so that the positions thereof coincide with each other. As shown in FIG. 5, the output disk 16 is provided with two plates each having an output-side protrusion 16c having a triangular cross section on one surface of both surfaces of the disk, and the other disk of the two plates. The surfaces are configured by bonding the output side protrusions 16c so that the positions thereof coincide with each other. The input disk 15 and the output disk 16 are manufactured by pressing a plate material to form a plate having a triangular cross section. In addition, as a material of the input / output disks 15 and 16, for example, a special alloy steel having high fatigue strength and high wear resistance is used. Moreover, in order to always hold | maintain an oil film between contact surfaces, lubricating oil is supplied to a contact part using centrifugal lubrication, scraping lubrication, etc.

  FIG. 6 is a plan view showing an urging force adjusting template and a cam follower of the multi-disc multi-stage transmission unit according to the first embodiment. 7A and 7B are diagrams showing an urging force adjustment state by the template and the cam follower of the multi-disc multi-stage transmission unit according to the first embodiment. FIG. 7A shows an urging force release state, and FIG. 7B shows a maximum urging force application state. The configuration of the biasing force adjusting means for the pressing rollers 17, 17 in the multi-disc multi-stage transmission unit T / U will be described below.

  As shown in FIG. 6, the pair of templates 28 and 28 slide in the pin axis direction with respect to the support pins 34 and 34 whose ends are fixed to the input shaft support frames 18 and 18 and the output shaft support frames 19 and 19, respectively. It is provided to be movable. The coil springs 30 and 30 are interposed at both ends of the pair of templates 28 and 28, and the urging force Fs by the coil springs 30 and 30 is set to act in a direction to separate the pair of templates 28 and 28 from each other. Yes.

  As shown in FIGS. 6 and 7, the pair of cam followers 29, 29 are set so that the biasing force Fd by the disc spring 22 acts on the contact surfaces of the pair of templates 28, 28 with the cam surfaces 28a, 28a. The That is, the urging force F applied to the pair of pressing rollers 17 and 17 is obtained from the urging force difference (Fd−Fs) between the urging force Fd by the disc spring 22 and the urging force Fs by the coil spring 30. By adjusting the surface shapes of the cam surfaces 28a, 28a of the pair of templates 28, 28, adjustment is made so as to obtain an optimum clamping pressing force corresponding to the speed change condition.

  The surface shapes of the cam surfaces 28a, 28a of the pair of templates 28, 28 are set as follows.

  First, when the pair of cam followers 29, 29 are in the reverse range position (REV) and the neutral range position (N) shown in FIG. 6, the contraction amount of the coil spring 30 is maximized as shown in FIG. 7 (a). By doing so, the urging force Fs by the coil spring 30 is set to be maximized.

  On the other hand, when the pair of cam followers 29, 29 are in the parking range position (P) shown in FIG. 6, as shown in FIG. The urging force Fs by 30 is set to be minimum.

  Furthermore, when the pair of cam followers 29, 29 are in the drive range position (D) shown in FIG. 6, the coil spring 30 is contracted stepwise from the first gear to the seventh gear, so that the coil spring 30 The urging force Fs is set so as to increase from the first gear to the seventh gear.

  In addition, when the pair of cam followers 29, 29 are in the drive range position (D) shown in FIG. 6, the coil spring 30 is temporarily moved during a shift to an adjacent shift stage (during upshift or downshift). Therefore, the biasing force Fs by the coil spring 30 during the shift is set to be larger than the biasing force Fs of the coil spring 30 at the shift stage before and after the shift.

Next, the operation will be described.
The operation of the multi-disc multi-stage transmission unit T / U of the first embodiment is described as “the principle of speed change using elastic deformation of the disk”, “advantage of the multi-stage transmission that transmits the driving force by the elastic deformation disk”, “R range selection” “Clutch action at time”, “Parking action when P range is selected”, “Starting action when switching N → D”, “Automatic shifting action when D range is selected”, “Shifting response improving action” .

[Speed change principle using elastic deformation of disk]
FIG. 8 is a principle explanatory plan view showing a shift principle using elastic deformation of the disk in the multi-disk multi-stage transmission unit T / U of the first embodiment. FIG. 9 is a principle explanatory front view showing a speed change principle using elastic deformation of the disk in the multi-disk multi-speed transmission unit T / U of the first embodiment.

  As shown in FIG. 8 and FIG. 9, a multi-stage transmission for explaining the speed change principle is provided on the input shaft, the disc-shaped input disk having the outer peripheral end disposed close to the output shaft, and the output shaft. A disk-shaped output disk whose end is arranged close to the input shaft, and a disk overlapping region where the input disk and the output disk overlap with each other, along an axis connecting line connecting the axis of the input shaft and the axis of the output shaft. And a pair of pressing means that sandwich and press both disks at a position corresponding to the required gear ratio and form a torque transmission contact portion by elastic deformation of both disks.

  In this multi-stage transmission, as shown in FIG. 8, when both discs are sandwiched and pressed by a pair of pressing means, the input disc and the output disc are partially elastically deformed to form a torque transmission contact portion. The That is, when a concentrated load is applied to a doubly supported beam (disk), the torque transmission contact portion is formed on the input / output disk using the principle that the beam at the portion where the concentrated load is applied is greatly bent.

  When the torque transmission contact portion is formed at an intermediate position (P1 position in FIG. 9) on the line connecting the axis of the input shaft and the axis of the output shaft, the input side drive radius R2 from the axis of the input side contact circle. Thus, the output side drive radius R2 from the axis of the output side contact circle becomes the same, and a constant speed ratio is obtained between the input shaft and the output shaft.

  Further, if the torque transmission contact portion is formed at the position (P2 position in FIG. 9) moved from the constant speed ratio position (P1 position in FIG. 9) to the input shaft side, the input from the shaft center of the input side contact circle is performed. The side drive radius R1 is shortened, the output side drive radius R3 from the axis of the output side contact circle is lengthened, and a reduction ratio (low side transmission ratio) is obtained between the input shaft and the output shaft.

  Further, when the torque transmission contact portion is formed at the position (P3 position in FIG. 9) moved from the constant speed ratio position (P1 position in FIG. 9) to the output shaft side, the input from the axis of the input side contact circle is input. The side drive radius R3 becomes longer, the output side drive radius R1 from the axis of the output side contact circle becomes shorter, and a speed increasing ratio (high side speed ratio) is obtained between the input shaft and the output shaft.

[Advantages of a multi-stage transmission that transmits driving force by an elastically deformable disk]
As described above, the multi-stage transmission of the present invention can be said to be a traction drive type multi-stage transmission that transmits a driving force by an elastically deformable disk. This multi-stage transmission exhibits a gear shifting function with a wide range of gear ratio setting freedom, a clutch function, and an efficient torque that can aim for cost reduction, weight reduction, and compactness. It has the advantage of being able to aim at cooling and lubrication of the transmission contact portion. Hereinafter, each advantage will be described.

(Shifting function)
The multi-stage transmission of the present invention exhibits a speed change function having a high degree of freedom in setting a speed ratio including the speed increasing ratio.
For example, the gear ratio setting range (ratio cover) is 8 to 11, and it is possible to meet the demand for multi-stage that aims to improve high-speed fuel consumption. In particular, when the constant speed ratio position is shifted to the speed increasing ratio side by a final reduction gear or the like, the speed ratio setting freedom on the speed reducing ratio side is further increased. Further, since the number of disks can be set freely, generalization can be aimed at, and transmission torque can be increased by adding the number of disks.

(Clutch function)
In the multi-stage transmission of the present invention, when the pressing force for holding and pressing both disks by the pressing means is released, the input disk and the output disk are returned to the flat plate disk by the elastic restoring force, and are formed by partial elastic deformation. There is no torque transmission contact. For this reason, torque transmission from the input shaft to the output shaft is interrupted, and a clutch function that switches between torque transmission from the input shaft to the output shaft and torque interruption from the input shaft to the output shaft is exhibited.
For example, in the case of a continuously variable transmission for a vehicle (belt CVT, toroidal CVT, etc.), since it always has a torque transmission contact portion and has only a speed change function, a clutch function such as a clutch mechanism or a torque converter to ensure a neutral state It is necessary to use parts together. On the other hand, in the multi-stage transmission of the present invention, it is possible to omit the clutch functional parts.

(Low cost, light weight, compact size)
In the multi-stage transmission of the present invention, the pressing force for sandwiching and pressing the disk is canceled by the torque transmission contact portion, and no load acts on the input shaft and the output shaft, so there is no need to have a structure with high rigidity, The input / output shaft can have a small diameter (also effective for increasing the gear ratio width), and the disk can be manufactured by press molding or the like using a thin steel plate.
Since the input / output shaft, the disk-shaped input / output disk, and the pressing means are used as components, the structure is simpler and the number of parts is smaller than that of a conventional Bayer transmission.
Only a small movable space is required to move the pressing means in the region between the input shaft and the output shaft, and the movable space is greatly reduced as compared with the conventional Bayer transmission.
Since the input disk and the output disk are superposed on each other, it is sufficient to ensure a unit length of more than 1.5 times the diameter of the disk, and the multi-stage transmission can be accommodated in a narrow space.
By these synergistic effects, it is possible to achieve cost reduction, weight reduction, and compactness in all aspects of cost, weight, and required space when compared with known multi-stage transmissions already installed in vehicles. it can.

(Cooling / lubrication function)
The multi-stage transmission of the present invention has a fixed input shaft and output shaft, and the torque transmission contact portion is concentrated in one place. It is possible to eliminate the need for an oil pump by utilizing centrifugal lubrication, scraping lubrication, or the like.

[Clutch action when R range is selected]
FIG. 10 is a plan view showing the positional relationship between the template and the cam follower when the R range is selected in the vehicle automatic transmission system to which the multi-disc multi-stage transmission unit T / U according to the first embodiment is applied.

  During reverse running by selecting the R range in the automatic transmission system for a vehicle, the clamping pressure by the pressing rollers 17 and 17 of the multi-disc multi-speed transmission unit T / U is released to cut off the torque transmission, and the coupling sleeve 8a of the synchro mechanism 8 is cut off. 1 to the right in FIG. 1, and the reverse gear 5 is fixed to the input shaft 3.

  That is, when the R range is selected, the pair of cam followers 29, 29 are in the reverse range position (REV) shown in FIG. 10 among the surface shapes of the cam surfaces 28a, 28a of the pair of templates 28, 28. At this time, the amount of contraction of the coil spring 30 is maximized, and accordingly, the urging force Fs of the coil spring 30 is maximized. Therefore, the urging force Fs of the coil spring 30 is equal to or slightly larger than the urging force Fd by the disc spring 22 (see FIG. 15). As a result, the biasing force difference (Fd−Fs) becomes almost zero, so that the disc clamping pressing by the pair of pressing rollers 17 and 17 is released, and the torque transmission by the multi-disc multi-stage transmission unit T / U is interrupted. That is, the clutch release function is exhibited.

  Therefore, when the R range is selected, as shown in FIG. 1, the drive torque from the engine 1 is such that the input shaft 3 → synchro mechanism 8 → reverse gear 5 → reverse idler gear 6 → output gear 7 → final gear 9 → differential gear unit. 10 → left and right drive shafts 11 and 12 → right and left drive wheels 13 and 14 are transmitted to achieve the first reverse speed.

[Parking action when P range is selected]
FIG. 11 is a plan view showing the positional relationship between the template and the cam follower when the P range is selected in the vehicle automatic transmission system to which the multi-disc multi-stage transmission unit T / U according to the first embodiment is applied. FIG. 12 is a front view showing a torque transmission contact portion formed on the disc when the P range is selected in the vehicle automatic transmission system to which the multi-disc multi-stage transmission unit T / U according to the first embodiment is applied.

  When the vehicle is stopped by selecting the P range in the automatic transmission system for a vehicle, the input / output discs 15 and 16 are fastened to each other so that the input / output discs 15 and 16 are fixedly connected together to be locked, A parking function for fixing the output shaft 4 is exhibited.

  That is, when the P range is selected, the pair of cam followers 29 and 29 are at the parking range position (P) shown in FIG. 11 among the surface shapes of the cam surfaces 28a and 28a of the pair of templates 28 and 28. At this time, the extension amount of the coil spring 30 is maximized, and accordingly, the biasing force Fs of the coil spring 30 is minimized. Therefore, when the biasing force difference (Fd−Fs) between the biasing force Fd of the disc spring 22 and the biasing force Fs of the coil spring 30 is maximized (see FIG. 15), the pair of pressing rollers 17 and 17 causes the input / output disk to be 15 and 16 are strongly held and pressed.

  As a result, as shown in FIG. 12, a plurality of torque transmission contact portions TC are formed around the set positions of the pair of pressing rollers 17 and 17 so that the input / output disks 15 and 16 do not allow relative rotation. It is said.

[Starting action when switching from N to D]
FIG. 13 is a plan view showing the positional relationship between the template and the cam follower when switching from the N range selection to the D range selection in the vehicle automatic transmission system to which the multi-disc multi-stage transmission unit T / U of the first embodiment is applied. a) shows when neutral is selected, (b) shows when neutral to 1st gear is selected, (c) shows when 1st gear full load is selected, and (d) shows when 1st gear is lightly loaded. (E) indicates the time when the first gear is selected to the second gear, and (f) indicates the time when the second gear is selected.

  When the N range is selected in the automatic transmission system for a vehicle, the clamping pressure by the pressing rollers 17 and 17 of the multi-disc multi-speed transmission unit T / U is released to interrupt the torque transmission, and the coupling sleeve 8a of the synchronization mechanism 8 is shown in FIG. The left stroke position of

  With this N range selection, when the pair of cam followers 29, 29 are at the neutral range position (N) shown in FIG. 13 (a) of the surface shapes of the cam surfaces 28a, 28a of the pair of templates 28, 28, By maximizing the amount of contraction of the coil spring 30, the urging force Fs of the coil spring 30 is maximized. Therefore, the biasing force Fs of the coil spring 30 is slightly larger than the biasing force Fd of the disc spring 22 (see FIG. 15), and as a result, the biasing force difference (Fd−Fs) becomes a negative value. The disc holding and pressing by the pair of pressing rollers 17 and 17 are released, and the torque transmission by the multi-disc multi-stage transmission unit T / U is cut off and the neutral state is established.

  Then, when switching from the N range selection to the D range selection, the pair of cam followers 29, 29 is the first speed as shown in FIG. 13 (b) among the surface shapes of the cam surfaces 28a, 28a of the pair of templates 28, 28. When moving toward the side, the urging force Fs of the coil spring 30 gradually decreases by gradually extending the coil spring 30 along with the movement. Therefore, the biasing force difference (Fd−Fs) between the biasing force Fd by the disc spring 22 and the biasing force Fs of the coil spring 30 increases, and the disc pressing force by the pair of pressing rollers 17 and 17 increases.

  At the time of switching from N to D, if it is determined that the accelerator opening is a full load due to the high opening range, the pair of cam followers 29 and 29 are connected to the cam surfaces 28a and 28a of the pair of templates 28 and 28, respectively. Among the surface shapes, the first-speed full load position shown in FIG. 13C is set, and the urging force Fs of the coil spring 30 is minimized by maximizing the extension amount of the coil spring 30. Therefore, when the biasing force difference (Fd−Fs) between the biasing force Fd of the disc spring 22 and the biasing force Fs of the coil spring 30 is the largest in all the shift speeds (see FIG. 15), the pair of pressing rollers 17, 17, the input / output discs 15 and 16 are clamped and pressed at the position where the first-stage input ridge 15a and the output-side ridge 16g intersect, and the vehicle can be started at full load with the first-speed gear ratio.

  At the time of switching from N to D, if it is determined that the accelerator opening is in a low opening range and the load is light, the pair of cam followers 29 and 29 are connected to the cam surfaces 28a and 28a of the pair of templates 28 and 28, respectively. Among the surface shapes, the first-speed light load position shown in FIG. 13 (d) is set, and the extension amount of the coil spring 30 is set to the maximum range, so that the urging force Fs of the coil spring 30 becomes slightly larger than that at the time of full load. Therefore, when the biasing force difference (Fd−Fs) between the biasing force Fd by the disc spring 22 and the biasing force Fs of the coil spring 30 becomes large next to the first full load (see FIG. 15), the pair of pressing rollers 17. , 17 can pinch and press the input / output discs 15 and 16 at a position where the first-stage input-side ridge 15a and the output-side ridge 16g intersect, and the vehicle can be started with a light load at the first-speed gear ratio.

  For adjusting the clamping pressure corresponding to the full load or the light load, this function is replaced with the setting of the surface shapes of the cam surfaces 28a, 28a of the pair of templates 28, 28, for example, the input torque from the engine 1 It is also possible to provide a loading cam that operates according to the size of the lens, and adjust the holding pressing force corresponding to the load by using the cam operation amount.

[Automatic shifting when D range is selected]
FIG. 14 is an enlarged cross-sectional view showing a torque transmission contact portion when the D range is selected in the vehicle automatic transmission system to which the multi-disc multi-stage transmission unit T / U according to the first embodiment is applied. FIG. 15 shows an urging force (= clamping pressing force) acting on the torque transmission contact portion at each gear position when the D range is selected in the vehicle automatic transmission system to which the multi-disc multi-speed transmission unit T / U according to the first embodiment is applied. It is a biasing force characteristic diagram showing the relationship.

  During forward traveling by selecting the D range in the automatic transmission system for a vehicle, as shown in FIG. 1, the driving torque from the engine 1 is input shaft 3 → multi-disc multi-speed transmission unit T / U → output shaft 4 → output gear 7 → Final gear 9 → Differential gear unit 10 → Left and right drive shafts 11 and 12 → Left and right drive wheels 13 and 14. At this time, the seventh forward speed is achieved by moving the clamping pressing position by the pressing rollers 17, 17 of the multi-disc multi-stage transmission unit T / U.

  For example, when traveling in the D range, if an upshift command from the first speed to the second speed is output, the pair of cam followers 29, 29 are moved from the first speed position in FIG. 13 (c) or FIG. 13 (d). When moving toward the second speed side as shown in FIG. 13 (e), the urging force Fs of the coil spring 30 gradually increases by gradually contracting the coil spring 30 with the movement. Therefore, the biasing force difference (Fd−Fs) between the biasing force Fd of the disc spring 22 and the biasing force Fs of the coil spring 30 is reduced, and the disc pressing force of the pair of pressing rollers 17 and 17 is reduced.

  And if it moves to the 2nd speed position shown in FIG.13 (f) among the surface shapes of the cam surfaces 28a and 28a of a pair of templates 28 and 28, the coil spring 30 will be extended, and the urging | biasing force Fs of the coil spring 30 will be extended. This is smaller than that during the shift in FIG. Therefore, the biasing force difference (Fd−Fs) between the biasing force Fd by the disc spring 22 and the biasing force Fs of the coil spring 30 is temporarily suppressed during the shift from the first speed to the second speed, and immediately before the second speed is reached. After a change of increasing again from the position, the pair of pressing rollers 17, 17 sandwich and press the input / output disks 15, 16 at the position where the second-stage input ridge 15 b and the output ridge 16 f intersect. It is possible to upshift to a high speed.

  When traveling at the second gear, as shown in FIG. 14, the input-side ridge 15 b and the output-side ridge 16 f that receive the clamping pressure at the second gear are arranged between the apexes 15 ′ and 16 ′ having a triangular cross section. Therefore, the contact width W (for example, about 2 mm) of the torque transmission contact portion is small, the contact shape is also substantially round, and the contact area is small. Accordingly, it is possible to suppress the spin loss of the transmission torque at the torque transmission contact portion TC that increases as the contact area increases.

  Further, since the apex portions 15 'and 16' of the triangular cross-sectional shape of the input-side ridge 15b and the output-side ridge 16f are formed as inclined top portions having a downward inclination angle in the axial direction, the opposing inclined top shapes are slightly It is pressed with a contact angle θ (for example, about 1.7 °). Accordingly, torque transmission is achieved by fitting the inclined surface while suppressing slippage, and high torque transmission efficiency can be achieved.

  The above automatic shifting action is from the 5th gear to the 6th gear (OD) when driving in the D range, when shifting up from 2nd gear to 3rd gear, when shifting up from 3rd gear to 4th gear. The same effect is exhibited during upshifting from 6th gear to 7th gear (super OD). Further, the same effect is exhibited at the time of each downshift when traveling in the D range.

As described above, when the pair of cam followers 29, 29 are in the drive range position (D) shown in FIG. 13, the coil spring 30 is contracted stepwise from the first gear to the seventh gear, The surface shapes of the cam surfaces 28a and 28a of the pair of templates 28 and 28 are set so that the urging force Fs of the coil spring 30 increases from the first gear to the seventh gear. With this setting, the biasing force difference (Fd−Fs) that becomes the clamping pressing force by the pair of pressing rollers 17, 17 is the largest when the first speed full load is selected, as shown in FIG. It gets smaller step by step as you go faster.
Therefore, in order to cope with the fact that the transmission torque at the first gear is the largest and the transmission torque at the seventh gear is the smallest, at each gear position from the first gear to the seventh gear, proper contact without slipping is achieved. A clamping pressing force for obtaining an area can be applied.

In addition, when the pair of cam followers 29, 29 are in the drive range position (D) shown in FIG. 13, the coil spring 30 is temporarily contracted during upshifting or downshifting shifting to the adjacent gear stage. Thus, the surfaces of the cam surfaces 28a, 28a of the pair of templates 28, 28 so that the urging force Fs of the coil spring 30 during the shift is larger than the urging force Fs of the coil spring 30 at the shift stage before and after the shift. The shape is set. With this setting, the biasing force difference (Fd−Fs) during the shift, which becomes the clamping pressing force by the pair of pressing rollers 17, 17, becomes smaller than the biasing force difference (Fd−Fs) at the shift stage before and after the shift.
Therefore, during the upshift from the first gear to the second gear or the downshift from the second gear to the first gear, etc., the torque required to move the pair of pressing rollers 17, 17 is reduced, and the gear shift By reducing the load on the stepping motor 23 for operation, a smooth automatic transmission can be performed while using the small stepping motor 23.

[Speed change response improving effect]
FIG. 16 is an operation explanatory diagram showing a minute steer effect that occurs during a downshift at the time of traveling in the D range in the vehicle automatic transmission system to which the multi-disc multi-stage transmission unit T / U according to the first embodiment is applied. FIG. 17 is an operation explanatory diagram showing a minute steer effect that occurs during an upshift during D-range traveling in the vehicle automatic transmission system to which the multi-disc multi-stage transmission unit T / U according to the first embodiment is applied.

  In the first embodiment, when the pair of pressing rollers 17 and 17 are fixed in position without any change in the shift speed, the roller rotation axis is maintained parallel to the shaft center connection line CL, and the position is moved by the change in the shift speed. The attachment allows fine tilting of the roller rotation axis in accordance with the moving direction along the axis connection line CL.

  Therefore, during the downshift during the D range traveling, as shown in FIG. 16, the pair of pressing rollers 17, 17 are rotated rightward from the imaginary line position to the solid line position in FIG. It shows a micro steer effect that tilts. Therefore, the force generated at the position of the disk contact point of the pressing rollers 17 and 17 is inclined, and a component force that coincides with the downshift direction DS indicated by the arrow in FIG. The shift speed can be accelerated and the shift response can be improved.

  In addition, during the upshift during the D range traveling, as shown in FIG. 17, the pair of pressing rollers 17, 17 is moved leftward from the imaginary line position to the solid line position in FIG. It shows a micro steer effect that tilts. Therefore, the force generated at the position of the disk contact point of the pressing rollers 17 and 17 is inclined, and a component force that coincides with the upshift direction US indicated by the arrow in FIG. The shift speed can be accelerated and the shift response can be improved.

  By the way, the time required for the full stroke from the first gear to the seventh gear or the time required for the full stroke from the seventh gear to the first gear is less than 1 second due to the minute steering action of the pressing rollers 17 and 17. It was confirmed to be completed in the required time.

Next, the effect will be described.
In the multi-disc multi-stage transmission unit T / U according to the first embodiment, the effects listed below can be obtained.

(1) An input shaft 3 connected to a prime mover (engine 1) and supported by a transmission case member (input shaft support frames 18, 18), and a transmission case member (output shaft) arranged in parallel to the input shaft 3. An output shaft 4 supported by support frames 19, 19), a disk-shaped input disk 15 provided on the input shaft 3 and having an outer peripheral end disposed close to the output shaft 4, and provided on the output shaft 4. , a disk-shaped output disk 16 of the perimetric edge arranged close to the input shaft 3, the input disc 15 and the output disk 16 of the disk overlapping area overlapping with each other, the axis O ₃ of the input shaft 3 the movably provided along the axis connecting line CL connecting the output shaft axis O ₄ of 4, both disks 15 and 16 sandwiching pressed by corresponding to required gear ratio position, the two discs 15 and 16 A pair forming the torque transmission contact part TC by elastic deformation A plurality of input side bumps formed concentrically at different radii from the axis O ₃ of the input shaft 3 on the disk surface. The output disk 16 includes a plurality of concentric grooves 15a, 15b, 15c, 15d, 15e, 15f, and 15g that are concentrically formed on the disk surface at different radii from the axis O ₄ of the output shaft 4. The plurality of input side ridges 16a, 16b, 16c, 16d, 16e, 16f, and 16g, the plurality of input side ridges 15a, 15b, 15c, 15d, 15e, 15f, and 15g and the plurality of output side ridges 16a. , 16b, 16c, 16d, 16e, 16f, and 16g are set such that the length of the shaft center connecting line CL is distributed to the input side driving radius and the output side driving radius according to a plurality of required transmission ratios. On connection line CL The tops of both ridges were placed opposite to each other. For this reason, while achieving cost reduction, weight reduction, and compactness, it is possible to exhibit both a gear shifting function with a high degree of freedom in setting a gear ratio including a speed increasing ratio and a clutch function for switching torque transmission / disconnection. In addition, the transmission torque spin loss can be reduced at each gear ratio position.

  (2) The plurality of input side protrusions 15a, 15b, 15c, 15d, 15e, 15f, 15g and the plurality of output side protrusions 16a, 16b, 16c, 16d, 16e, 16f, 16g The height of the ridge was set to be the highest, and the height of the ridge was gradually lowered toward the outer peripheral side. For this reason, when the clamping pressing force to the disk by the pair of pressing rollers 17 and 17 is released, a gap between the opposing input side ridge and the output side ridge can be secured, and friction loss due to drag can be reduced.

  (3) The plurality of input side ridges 15a, 15b, 15c, 15d, 15e, 15f, 15g and the plurality of output side ridges 16a, 16b, 16c, 16d, 16e, 16f, 16g have a triangular cross-sectional shape. The apexes 15 ′ and 16 ′ are inclined apex shapes having a downward inclination angle in the axial direction, and the opposing inclined apex shapes are pressed with a contact angle θ. For this reason, even if the disc flatness varies, the contact shape can be stabilized by elastic deformation and the triangular cross-section ridge, and the torque transmission action by the inclined surface fitting that suppresses the slip is shown. High torque transmission efficiency can be achieved.

  (4) The input disk 15 and the output disk 16 are configured by forming a ridge having a triangular cross section on one surface of the disk plane and bonding the other surfaces of the two disk planes together. For this reason, it is possible to achieve both an increase in rigidity and a reduction in weight of the input disk 15 and the output disk 16 each having a triangular cross section. In addition, since a space is formed in the protruding portion, this space can be used as a resin-filled space for heat dissipation.

  (5) The input disk 15 and the output disk 16 are manufactured by pressing from a plate material to form a plate having a triangular section. For this reason, the input disk 15 and the output disk 16 in which the protrusions having a triangular cross section are formed can be manufactured at a low cost.

  (6) The input shaft 3 includes a primary disk group 150 configured by arranging a plurality of input disks 15 in the axial direction, and the output shaft 4 includes a plurality of output disks 16 in the axial direction. The pair of pressing means (pressing rollers 17, 17) insert the output disk 16 into each of the adjacent axial gaps of the plurality of input disks 15. By disposing, the primary disk group 150 and the secondary disk group 160 form a disk overlapping area where they overlap each other, and are sandwiched and pressed from both sides of this disk overlapping area. Therefore, by setting the number of input disks 15 and the number of output disks 16, it is possible to cope with the required transmission torque capacity, and it is possible to reduce the clamping pressure by increasing the number of disks.

  The multi-stage transmission according to the present invention has been described based on the first embodiment. However, the specific configuration is not limited to the first embodiment, and the gist of the invention according to each claim of the claims. As long as they do not deviate, design changes and additions are permitted.

  In the first embodiment, an example of a multi-disk having a primary disk group 150 constituted by a plurality of input disks 15 and a secondary disk group 160 constituted by a plurality of output disks 16 is shown. However, as an example of a single disk with one input disk and one output disk, or an example of a double disk with one input disk and one output disk, or one double disk with one input disk and two output disks. good.

  In the first embodiment, the input side ridges 15a, 15b, 15c, 15d, 15e, 15f, and 15g are formed on the input disk 15, and the output side ridges 16a, 16b, 16c, 16d, 16e, 16f, An example is shown in which a multistage transmission having seven speeds is formed by forming 16 g and applying a clamping pressing force at a stepwise pressing position by a pair of pressing rollers 17 and 17. However, a multi-stage transmission other than the seventh speed stage may be used by setting the number of protrusions.

  In Example 1, the example which uses the press roller 17 as a press means was shown. However, as the pressing means, other means such as a pressing pin or a pressing ball having a spherical tip may be used.

  In the first embodiment, a clamping pressing force is applied to the pair of pressing rollers 17 and 17 by the disc spring 22, and the clamping pressing force is adjusted using the templates 28 and 28 and the cam followers 29 and 29, and the disc spring 22 and the coil spring 30. An example is shown in which the difference in biasing force is applied. However, an example in which the clamping pressing force is applied by hydraulic pressure and the clamping pressing force is adjusted by hydraulic pressure adjustment is also possible.

  In the first embodiment, the stepping motor 23 and the screw screw 24 are used as means for moving the moving frame 21 for shifting. However, the moving frame 21 may be moved by a hydraulic actuator for shifting.

  In the first embodiment, an example of a multi-disc multi-stage transmission unit T / U applied to an automatic transmission system for an engine vehicle is shown as a multi-stage transmission of the present invention. However, the present invention can be applied not only to engine vehicles but also to multistage transmissions of other vehicles such as hybrid vehicles, electric vehicles, and fuel cell vehicles. In addition, by adjusting the number of discs (one to several) according to the torque capacity to be transmitted, it can be applied not only to vehicles but also to multistage transmissions installed in various devices. can do.

1 is an overall schematic diagram illustrating an automatic transmission system for a vehicle to which a multi-disc multi-stage transmission unit T / U (an example of a multi-stage transmission) according to a first embodiment is applied. 1 is an overall perspective view showing a multi-disc multi-stage transmission unit T / U according to Embodiment 1. FIG. FIG. 3 is a cross-sectional view taken along line AA of FIG. 2 illustrating the multi-disc multi-stage transmission unit T / U according to the first embodiment. FIG. 4 is an enlarged cross-sectional view of a portion B in FIG. 3 illustrating an end interval holding structure of the input / output disc of the multi-disc multi-stage transmission unit according to the first embodiment. FIG. 4 is an enlarged cross-sectional view of a portion C in FIG. 3 showing a detailed structure of an input / output disk of the multi-disk multi-stage transmission unit of the first embodiment. It is a top view which shows the template and cam follower for urging | biasing force adjustment of the multi disk multistage transmission unit of Example 1. FIG. FIG. 3 is a diagram illustrating an urging force adjustment state by a template and a cam follower of the multi-disc multi-stage transmission unit according to the first embodiment, in which (a) represents an urging force release state and (b) represents a maximum urging force application state. FIG. 3 is a principle explanatory plan view showing a speed change principle using elastic deformation of a disk in the multi-disk multi-stage transmission unit T / U according to the first embodiment. FIG. 2 is a principle explanatory front view showing a speed change principle using elastic deformation of a disk in the multi-disk multi-stage transmission unit T / U according to the first embodiment. It is a top view which shows the positional relationship of the template and cam follower at the time of R range selection in the automatic transmission system for vehicles to which the multi disc multi-stage transmission unit T / U of Example 1 is applied. It is a top view which shows the positional relationship of the template and cam follower at the time of P range selection in the automatic transmission system for vehicles to which the multi disc multi-stage transmission unit T / U of Example 1 is applied. FIG. 3 is a front view showing a torque transmission contact portion formed on the disc when the P range is selected in the automatic transmission system for a vehicle to which the multi-disc multi-stage transmission unit T / U according to the first embodiment is applied. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a plan view showing a positional relationship between a template and a cam follower when switching from N range selection to D range selection in an automatic transmission system for a vehicle to which a multi-disc multi-speed transmission unit T / U of Example 1 is applied. (B) represents the selection from neutral to 1st gear, (c) represents the 1st gear full load selection, (d) represents the 1st gear light load selection, e) shows the selection from the first gear to the second gear, and (f) shows the second gear selection. It is an expanded sectional view showing a torque transmission contact part at the time of D range selection in an automatic transmission system for vehicles to which multi disk multi-stage transmission unit T / U of Example 1 is applied. The relationship of the urging | biasing force (= clamping pressure) which acts on a torque transmission contact part in each gear stage at the time of D range selection in the automatic transmission system for vehicles to which the multi-disc multi-speed transmission unit T / U of Embodiment 1 is applied is shown. It is a biasing force characteristic diagram. It is an operation explanatory view showing a minute steer effect generated during a downshift at the time of traveling in the D range in the automatic transmission system for a vehicle to which the multi-disc multi-stage transmission unit T / U of the first embodiment is applied. It is an operation explanatory view showing a minute steer effect generated during an upshift at the time of traveling in the D range in the automatic transmission system for a vehicle to which the multi-disc multi-stage transmission unit T / U of the first embodiment is applied.

Explanation of symbols

T / U multi-disc multi-speed transmission unit (multi-speed transmission)
1 engine (motor)
3 Input shaft 4 Output shaft 15 Input disk
150 Primary disk group 15a, 15b, 15c, 15d, 15e, 15f, 15g Input side protrusion 15 'Top 16 Output disk
160 Secondary disk group 16a, 16b, 16c, 16d, 16e, 16f, 16g Output side protrusion 16 'Top 17, 17 Press roller (pressing means)
18, 18 Input shaft support frame (transmission case member)
19, 19 Output shaft support frame (transmission case member)
21 Moving frame 22 Disc spring (biasing means)
23 Stepping motor (motor actuator)
24 Screw screw
O ₃ Input shaft 3 axis
O ₄ Output shaft 4 axis
CL shaft connection line
TC Torque transmission contact part θ Contact angle

Claims (6)

An input shaft connected to the prime mover and supported by the transmission case member;
An output shaft disposed in parallel to the input shaft and supported by a transmission case member;
A disc-shaped input disk provided on the input shaft and having an outer peripheral end disposed close to the output shaft;
A disc-shaped output disk provided on the output shaft and having an outer peripheral end disposed close to the input shaft;
Of the disk overlap region where the input disk and the output disk overlap each other, the input disk and the output disk are provided so as to be movable along an axis connection line connecting the axis of the input shaft and the axis of the output shaft. A pair of pressing means that sandwich and press both discs at a position and form a torque transmission contact portion by elastic deformation of both discs,
The input disk has a plurality of input side protrusions formed concentrically at different radii from the axis of the input shaft on the disk surface;
The output disk has a plurality of output-side protrusions formed concentrically at different radii from the axis of the output shaft on the disk surface;
The plurality of input-side ridges and the plurality of output-side ridges are set such that the length of the shaft connection line is divided into an input-side drive radius and an output-side drive radius according to a plurality of required speed ratios, A multi-stage transmission characterized in that the tops of both ridges are arranged opposite to each other on an axis connecting line. The multi-stage transmission according to claim 1, wherein
The plurality of input side ridges and the plurality of output side ridges are set such that the height of the ridges on the shaft side is the highest and the height of the ridges gradually decreases toward the outer peripheral side. Multi-stage transmission characterized by In the multi-stage transmission according to claim 1 or 2,
The plurality of input-side ridges and the plurality of output-side ridges have a triangular cross-sectional top having an inclined top shape having a downward inclination angle in the axial direction, and the opposing inclined top shapes having a contact angle. A multi-stage transmission characterized by pressing. The multi-stage transmission according to any one of claims 1 to 3,
The input disk and the output disk are formed by forming a protrusion having a triangular cross-section on one surface of the disk plane, and bonding the other surfaces of the two disk planes to each other. transmission. The multi-stage transmission according to claim 4, wherein
The multi-stage transmission is characterized in that the input disk and the output disk are manufactured by pressing from a plate material to form a plate having a triangular section. The multi-stage transmission according to any one of claims 1 to 5,
The input shaft has a primary disk group configured by arranging a plurality of input disks in the axial direction;
The output shaft has a secondary disk group configured by arranging a plurality of output disks in the axial direction;
The pair of pressing means forms a disk overlap region in which the primary disk group and the secondary disk group overlap each other by inserting and arranging output disks in each of adjacent axial gaps of the plurality of input disks, A multi-stage transmission characterized in that it is clamped and pressed from both side positions of the disk overlapping region.

Images