JP5736426B2 - Multi-disc transmission - Google Patents

Description

  The present invention relates to a multi-disc transmission.

  In Patent Document 1, a primary disk provided on the input shaft and a secondary disk provided on the output shaft are partially overlapped to provide a disk overlap area, and both disks are sandwiched between a pair of pressing rollers in this area. A multi-disc transmission that transmits the rotation of an input shaft to an output shaft by bringing them into contact is disclosed.

  In a multi-disc transmission, a shift is realized by changing the position where a pair of pressing rollers sandwiches both disks. If the position where both disks are sandwiched is close to the input shaft, the transmission ratio is low (the transmission ratio is large). ), The gear ratio changes to the High side (the gear ratio small side) when it approaches the output shaft.

JP 2010-53995 A

  In the multi-disc transmission disclosed in Patent Document 1, the pressing roller is rotatably supported by the moving frame, and the moving frame is moved along an axis connecting line that connects the input shaft and the output shaft. Shifting is realized by changing the position where the pressing roller sandwiches both disks.

  However, if the rotation axis of the pressing roller and the shaft coupling line are displaced due to dimensional variation or the like (see FIG. 3A), the displacement between the direction of the circumferential speed of the disk and the direction of rotation of the pressing roller at the portion where the pressing roller contacts the disk The friction due to this deviation acts between the pressing roller and the disk. Such friction is not preferable because it reduces the transmission efficiency of the transmission and increases the energy required to move the pressing roller during shifting.

  The present invention has been made in view of such a technical problem, and suppresses an increase in friction between the pressing roller and the disk due to a displacement of the rotating shaft of the pressing roller and the shaft connecting line due to dimensional variation or the like. With the goal.

  According to an aspect of the present invention, there is provided a multi-disc transmission, an input shaft to which rotation from a power source is input, an output shaft disposed in parallel to the input shaft, and the input shaft. A primary disk, a secondary disk provided on the output shaft and having a disk overlapping area overlapping the primary disk, and a pair of pressing rollers disposed on both sides of the primary disk and the secondary disk in the disk overlapping area And a pair of roller support portions that rotatably support the pair of pressing rollers, and the primary disk and the secondary disk overlap each other than a position where the pair of pressing rollers contact the primary disk and the secondary disk. The primary disk and A pair of trunnions that support the pair of roller support portions so as to be swingable about a swing axis that is orthogonal to the disk surface of the secondary disk, and a direction in which the pair of trunnions approach the primary disk and the secondary disk, respectively. And a pressing mechanism that presses the pair of pressing rollers against the primary disk and the secondary disk, respectively, and a speed change actuator that moves the pair of trunnions between the input shaft and the output shaft. A multi-disc transmission is provided.

  According to the above aspect, even if the rotation shaft of the pressing roller is deviated from the shaft coupling line due to dimensional variation or the like, the pressing roller swings by the roller support portion swinging, and the pressing roller rotation shaft rotates the disk. Since it faces the center, the deviation between the direction of the peripheral speed of the disk and the direction of rotation of the pressing roller at the contact portion is eliminated. Accordingly, it is possible to suppress a decrease in transmission efficiency due to the friction caused by the deviation acting between the pressing roller and the disk, and an increase in energy required to move the pressing roller during shifting.

  Further, since the pressing roller swings around the swing center, the distance between the rotating shaft of the pressing roller and the shaft connecting line is kept substantially constant. Therefore, an increase in deviation between the circumferential speed direction of the primary disk and the circumferential speed of the secondary disk at the contact portion due to an increase in the distance between the rotation shaft of the pressing roller and the shaft coupling line is suppressed, and the slip ratio is increased. As a result, a decrease in transmission efficiency can be suppressed.

1 is an overall schematic view of a vehicle including a multi-disc transmission. It is the figure which showed the disk superposition | polymerization area | region. It is the figure which showed the state which the rotating shaft of the pressing roller shifted | deviated from the shaft connection line. FIG. 5 is a diagram showing a state in which the pressing roller swings and the rotation axis of the pressing roller coincides with the rotation center of the disk (the distance between the pressing roller and the shaft coupling line is small). FIG. 6 is a diagram showing a state in which the pressing roller swings and the rotation axis of the pressing roller coincides with the rotation center of the disk (the distance between the pressing roller and the shaft connecting line is large). It is the figure which looked at the roller support structure from the substantially axial direction of the input shaft and the output shaft. It is the figure which looked at the roller support frame from the approximate rotation axis direction of the pressing roller. It is the figure which showed the shim interposed between a trunnion and a trunnion holding | maintenance part.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  FIG. 1 is an overall schematic view of a vehicle including a multi-disc transmission according to an embodiment of the present invention.

  The vehicle 1 includes an engine 2 as a power source, a multi-disc transmission (hereinafter referred to as a transmission) 3, left and right drive shafts 4 and 5, and left and right drive wheels 6 and 7.

  The transmission 3 includes a transmission case 9, an input shaft 10, a primary disk 11, a secondary disk 12, a pressing roller 13, an output shaft 14, a dry start clutch 15, a reverse gear 16, and a reverse idler gear. 17, an output gear 18, a sleeve 19, a final gear 20, and a differential gear unit 21.

  The input shaft 10 is provided coaxially with the engine 2, and the output shaft 14 is provided parallel to the input shaft 10. Each of the input shaft 10 and the output shaft 14 is rotatably supported by the transmission case 9.

  The primary disk 11 is composed of a plurality of circular disks and is fixed to the input shaft 10. Similarly, the secondary disk 12 is composed of a plurality of circular disks and is fixed to the output shaft 14. The primary disk 11 and the secondary disk 12 are arranged alternately so as to form an area in which the disks 11 and 12 partially overlap (hereinafter referred to as “disk overlap area”) (see FIG. 2). ).

  The pressing roller 13 is disposed on both sides of the primary disk 11 and the secondary disk 12, and is rotatably supported by the roller support frame 22 via a rotating shaft 13s and a bearing 13b. The roller support frame 22 is swingably coupled to the trunnion 23, which will be described later.

  When a force is applied to the trunnion 23 from a pressing mechanism 24 (see FIG. 4) described later, the trunnion 23 is displaced in a direction approaching the primary disk 11 and the secondary disk 12, and the pressing roller 13 is interposed via the trunnion 23 and the roller support frame 22. Thus, the pressing roller 13 is pressed against the primary disk 11 and the secondary disk 12. Thereby, the primary disk 11 and the secondary disk 12 are elastically deformed and contacted, and the rotation of the input shaft 10 is transmitted to the output shaft 14 via the primary disk 11 and the secondary disk 12.

  The trunnion 23 can be moved along a shaft connection line O (see FIG. 2) connecting the input shaft 10 and the output shaft 14 by the speed change actuator 30.

  The transmission actuator 30 includes a feed screw mechanism 31 and a motor 32 that rotates the feed screw of the feed screw mechanism 31. When the motor 32 is driven to move the trunnion 23 along the shaft coupling line O and the position where the pressing roller 13 sandwiches the primary disk 11 and the secondary disk 12 is changed to the input shaft 10 side, the transmission ratio of the transmission 3 becomes Low. On the other hand, when the output shaft 14 side is changed, the transmission gear ratio of the transmission 3 is changed to the High side (small transmission ratio side).

  The rotation shaft 13s of the pressing roller 13 is ideally disposed on the shaft coupling line O as shown in FIG. 2 when viewed from a direction orthogonal to the disk surface. As shown in FIG. 3A, when the rotation shaft 13s of the pressing roller 13 deviates from the shaft connecting line O, the disk (the secondary disk 12 in the present embodiment) in contact with the pressing roller 13 contacts the pressing roller 13. The deviation between the direction of the circumferential speed and the rotation direction of the pressing roller 13 becomes large, and the friction caused by this deviation acts between the pressing roller 13 and the disk, and the pressing roller 13 is moved during the reduction of transmission efficiency or at the time of shifting. This is because it leads to an increase in the energy required for this.

  For this reason, when a deviation occurs due to dimensional variation or the like, as shown in FIG. 3B, the pressing roller 13 swings so that the rotating shaft 13s of the pressing roller 13 is in contact with the center of rotation of the disk with which the pressing roller 13 contacts In the embodiment, it is preferable to face the center of the output shaft 14 so that the deviation between the disk circumferential speed direction and the rotation direction of the pressing roller 13 at the contact portion is eliminated.

  Further, there are a plurality of positions of the pressing roller 13 where such a shift is eliminated, along the circumferential direction of the disk with which the pressing roller 13 contacts, for example, a position greatly deviating from the shaft coupling line O as shown in FIG. 3C. In this case, the discrepancy between the direction of the circumferential speed of the disk and the rotation direction of the pressing roller 13 is eliminated. However, the further away the pressing roller 13 is from the shaft connection line O, the greater the deviation between the direction of the peripheral speed of the primary disk 11 and the direction of the peripheral speed of the secondary disk 12 at the contact portion, and the increase in slip ratio and thus transmission. It causes a decrease in efficiency.

  Therefore, when the pressing roller 13 is configured to swing, the shaft connection line O of the pressing roller 13 does not increase even if the pressing roller 13 swings so that the displacement of the pressing roller 13 from the shaft connection line O does not increase. It is preferable to employ a structure that regulates displacement in a direction away from the head.

  In the present embodiment, in view of the above points, the following roller support structure is adopted.

  FIG. 4 is a view of the roller support structure as viewed from the substantially axial direction of the input shaft 10 and the output shaft 14. FIG. 5 is a view of the roller support frame 22 as viewed from the direction of the substantial rotation axis of the pressing roller 13. In order to facilitate understanding, the trunnion 23 arranged on the front side in FIG. 5 is omitted in FIG.

  The roller support frame 22 is a rectangular frame having a space for accommodating the pressing roller 13 on the inner side, and the rotation shaft 13s of the pressing roller 13 is supported on the side surface. The roller support frame 22 has an end portion on the disk surface where the polymerization of the primary disk 11 and the secondary disk 12 starts from the contact position between the pressing roller 13 and the secondary disk 12 (hereinafter referred to as disk polymerization start side). It is connected to the trunnion 23 via a pin 25 extending in the orthogonal direction.

  The trunnion 23 is a plate-like member arranged in parallel to the disk surface. The trunnion 23 is provided on the end surface 23a on the position side where the superposition of the primary disk 11 and the secondary disk 12 ends (hereinafter referred to as “disk superposition end side”) and on the surface 23b facing the disk surface on the disk superposition end side as necessary As shown in FIG. 6, with the shims 33a and 33b interposed, the trunnion holding portion 26 is connected by bolts.

  The trunnion holding part 26 is supported so as to be slidable in the axial direction on a guide shaft 27 arranged in parallel to the shaft connection line O and to be rotatable about the guide shaft 27. Thereby, the trunnion 23 can move along the axis connecting line O and can move in a direction approaching the disk surface.

  A central opening 23c larger than the outer shape of the roller support frame 22 is formed in the center of the trunnion 23, and the roller support frame 22 is accommodated in the central opening 23c. Since the center opening 23 c is larger than the outer shape of the roller support frame 22, a gap is formed between the roller support frame 22 and the inner wall of the center opening 23 c, and the roller support frame 22 may swing around the pin 25. Permissible.

  Further, the width of the central opening 23c on the disk polymerization end side is narrower than other portions. Thus, when the swing angle of the roller support frame 22 reaches a predetermined swing angle, the corner portion on the polymerization end position side of the roller support frame 22 comes into contact with the inner wall 23s on the disk polymerization end side of the central opening 23c, and the roller The swing angle of the support frame 22 is restricted from increasing beyond a predetermined swing angle. That is, the inner wall 23 s on the polymerization end position side of the central opening 23 c functions as a stopper that regulates the maximum swing angle of the roller support frame 22.

  Further, the trunnion 23 is formed with side openings 23d extending along the shaft connection line O on both sides of the central opening 23c. Even if the trunnion 23 moves along the shaft connection line O, the trunnion 23 and the input shaft 10 and the output shaft 14 do not interfere with each other.

  A pressing force receiving portion 23e is connected to the end of the trunnion 23 on the disk polymerization start side. The arm 28 is in contact with the pressing force receiving portion 23e. When a pressing force is applied from the pressing mechanism 24 to one end of the arm 28, the arm 28 rotates about the hinge pin 29, and a force is applied from the arm 28 to the pressing force receiving portion 23 e of the trunnion 23 to support the trunnion 23 and the roller. A pressing force acts on the pressing roller 13 via the frame 22. As a result, the pressing roller 13 is pressed against the primary disk 11 and the secondary disk 12.

  Thus, in this embodiment, the roller support frame 22 can be swung around the pin 25 orthogonal to the disk surface on the disk polymerization start side from the position where the pressing roller 13 contacts the primary disk 11 and the secondary disk 12. The trunnion 23 was supported. Thereby, even if the rotation shaft 13s of the pressing roller 13 is deviated from the shaft connecting line O due to dimensional variation or the like, the pressing roller 13 swings and the rotation shaft 13s of the pressing roller 13 faces the rotation center of the secondary disk 12, The deviation between the circumferential speed direction of the secondary disk 12 and the rotation direction of the pressing roller 13 at the contact portion is eliminated.

  Accordingly, it is possible to suppress a decrease in transmission efficiency and an increase in energy required to move the pressing roller 13 during a shift due to the friction caused by the deviation acting between the secondary disk 12 and the pressing roller 13. (Effect corresponding to claim 1).

  Further, since the pressing roller 13 swings around the pin 25, the distance between the rotating shaft 13s of the pressing roller 13 and the shaft connecting line O is kept substantially constant before and after the swinging. As a result, an increase in deviation between the circumferential speed direction of the primary disk 11 and the circumferential speed direction of the secondary disk 12 at the contact portion due to an increase in the distance between the rotation shaft 13s of the pressing roller 13 and the shaft coupling line O is suppressed. In addition, an increase in the slip ratio and a decrease in the transmission efficiency can be suppressed (effect corresponding to claim 1).

  Further, the swinging angle of the pressing roller 13 changes when the pressing roller 13 moves by shifting. If the swinging angle of the pressing roller 13 is large at this time, the pressing roller 13 may swing greatly when the swinging direction is reversed, and the movement of the pressing roller 13 may become unstable.

  However, in the present embodiment, the inner wall 23s of the central opening 23c on the disk overlapping end side functions as a stopper, and the maximum swing angle of the roller support frame 22 that supports the pressing roller 13 is regulated. Thereby, it is possible to prevent the movement of the pressing roller 13 from becoming unstable (effect corresponding to claim 2).

  In addition, the trunnion 23 and the trunnion holding portion 26 are connected to the end surface 23a on the disc polymerization end side of the trunnion 23 and a surface 23b facing the disc surface with shims 33a and 33b interposed as necessary. .

  Accordingly, by changing the presence / absence of the shim 33a and the thickness of the shim 33a disposed on the end surface 23a of the trunnion 23 on the disk polymerization end side, the deviation between the rotating shaft 13s of the pressing roller 13 and the shaft connecting line O is reduced. The friction caused by the deviation acts between the pressing roller 13 and the disk surface, so that it is possible to further suppress a decrease in transmission efficiency and an increase in energy required to move the pressing roller 13 during shifting. Effect corresponding to claim 3).

  Further, the distance between the pressing roller 13 and the disk surface can be adjusted to the design value by changing the presence / absence of the shim 33b arranged on the surface 23b facing the disk surface and the thickness of the shim 33b. Thus, the force acting on the disk surface from the pressing roller 13 when the pressing force is applied by the pressing mechanism 24 can be optimized (effect corresponding to claim 4).

  The embodiment of the present invention has been described above, but the above embodiment is merely one example of application of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. is not.

  For example, in the above embodiment, the trunnion 23 is configured to move closer to the primary disk 11 and the secondary disk 12 by rotating the trunnion 23 about the guide shaft 27. It may be configured to move in a direction orthogonal to the direction.

3 Multi-disc transmission 10 Input shaft 11 Primary disc 12 Secondary disc 13 Pressing roller 13s Rotating shaft 14 Output shaft 22 Roller support frame (roller support portion)
23 trunnion 23s inner wall (stopper)
24 Pressing Mechanism 25 Oscillating Shaft 26 Trunnion Holding Part 33a Shim 33b Shim 30 Variable Speed Actuator O Shaft Connection Line

Claims (4)

A multi-disc transmission,
An input shaft to which rotation from a power source is input;
An output shaft disposed parallel to the input shaft;
A primary disk provided on the input shaft;
A secondary disk provided on the output shaft and having a disk overlap area overlapping the primary disk;
A pair of pressing rollers disposed on both sides of the primary disk and the secondary disk in the disk overlapping region;
A pair of roller support portions for rotatably supporting the pair of pressing rollers, respectively;
Oscillation perpendicular to the disk surfaces of the primary disk and the secondary disk on a position side where the primary disk and the secondary disk start to overlap with respect to a position where the pair of pressing rollers contact the primary disk and the secondary disk A pair of trunnions that pivotably support the pair of roller support portions around an axis; and
A pressing mechanism for displacing the pair of trunnions in a direction approaching the primary disk and the secondary disk, respectively, and pressing the pair of pressing rollers against the primary disk and the secondary disk, respectively;
A transmission actuator that moves the pair of trunnions between the input shaft and the output shaft;
A multi-disc transmission comprising: The multi-disc transmission according to claim 1,
Each of the pair of trunnions has a stopper that regulates the maximum swing angle of the pair of roller support portions,
A multi-disc transmission characterized by that. The multi-disc transmission according to claim 1 or 2,
A pair of trunnion holding portions that are movable in parallel with respect to an axis connecting line connecting the input shaft and the output shaft;
The pair of trunnion holding portions are respectively connected to the end surfaces of the pair of trunnions on the side where the primary disk and the secondary disk finish polymerization, and are detachable between the end surfaces and the pair of trunnion holding portions, respectively. Shim is inserted,
A multi-disc transmission characterized by that. The multi-disc transmission according to any one of claims 1 to 3,
A pair of trunnion holding portions that are movable in parallel with respect to an axis connecting line connecting the input shaft and the output shaft;
The pair of trunnion holding portions are respectively connected to surfaces of the pair of trunnions facing the disk surface, and detachable shims are interposed between the surfaces facing the disk surface and the pair of trunnion holding portions, respectively. To be
A multi-disc transmission characterized by that.

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