JP2006090405A - Gear shifter - Google Patents

Gear shifter Download PDF

Info

Publication number
JP2006090405A
JP2006090405A JP2004275768A JP2004275768A JP2006090405A JP 2006090405 A JP2006090405 A JP 2006090405A JP 2004275768 A JP2004275768 A JP 2004275768A JP 2004275768 A JP2004275768 A JP 2004275768A JP 2006090405 A JP2006090405 A JP 2006090405A
Authority
JP
Japan
Prior art keywords
shift
neutral
cam
stopper
force
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP2004275768A
Other languages
Japanese (ja)
Inventor
Yoshinobu Shiomi
Masaki Yoneyama
欣宣 塩見
正樹 米山
Original Assignee
Honda Motor Co Ltd
本田技研工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Honda Motor Co Ltd, 本田技研工業株式会社 filed Critical Honda Motor Co Ltd
Priority to JP2004275768A priority Critical patent/JP2006090405A/en
Publication of JP2006090405A publication Critical patent/JP2006090405A/en
Pending legal-status Critical Current

Links

Images

Abstract

<P>PROBLEM TO BE SOLVED: To allow easy change-over operation into a neutral condition by providing a stopper-operated neutral cam plate at one end of a shift drum for restricting a neutral corresponding position of the drum to obtain an optimum clicking feel at the neutral corresponding position in the rotation of the shift drum. <P>SOLUTION: The neutral cam plate 8 is provided at one end of the shift drum 4, and a cam groove 8a corresponding to a neutral shift position is formed in the outer periphery of the cam plate 8. A stopper roller 9a of a stopper mechanism 9 has pressure contact with the cam groove 8a. The optimum clicking feel in the rotation of the shift drum 4 is obtained by adjusting the pressure contact force of the stopper mechanism 9. This allows easy change-over operation into the neutral condition. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a transmission, and more particularly to an improved technique of a stopper mechanism in intermittent driving of a shift drum of a transmission for a motorcycle.

As a shift drum of a transmission for a motorcycle, a shift drum equipped with a star cam having a position restriction cam recess corresponding to a shift shift stage that rotates together with the drum is known, and in this shift drum, Position regulation at a predetermined shift shift stage in the rotation of the shift drum is performed by press-engaging a roller member of a stopper mechanism with a cam recess corresponding to the shift shift stage of the star cam (for example, Patent Document 1). reference).
However, in such a known shift drum, an improvement measure is taken from the viewpoint of adjustment of the moderation feeling at the neutral shift position because of the ease of setting the neutral shift position in the shifting operation, that is, the ease of switching to the neutral state. As a concrete measure of the improvement measure, there is not much known that has a mechanism for adjusting the pressure contact engagement force of the roller member of the cam contact described above.
JP 56-116955 A (2nd page-3rd page, Fig. 3)

  By the way, in dog missions using a manual clutch, the ease of setting the neutral shift position, that is, the ease of switching to the neutral state is important, but the neutral shift position in the intermittent drive of the shift drum is important. After all, the ease of switching depends on the magnitude of the pressure contact engagement force (load moderation) of the stopper roller that elastically contacts the stopper cam portion corresponding to the neutral shift position.

  However, in the shift drum using the star cam in which the stopper cam portion corresponding to the neutral shift position is disposed between the cam recesses corresponding to the first speed and second speed shift positions as in the invention described in Patent Document 1 described above. If the roller pressure contact force (elastic contact force) to the stopper cam is made too strong with emphasis on the ease of setting the neutral shift position, that is, the ease of switching to the neutral state, between the two gears across the neutral shift position, There is a possibility that it is difficult to switch gears in the first speed and the second speed shift.

  Therefore, in the star cam in which the stopper cam portion corresponding to the neutral shift position is disposed between the corresponding cam concave portions of the first speed and the second speed shift, a pressing element such as a stopper roller to the cam portion of the star cam is provided. The pressure contact load mode can be adjusted as appropriate, and the load mode to the stopper cam corresponding to the neutral shift position is selectively adjusted as needed, ensuring the reliability of the shifting operation and easy switching to the neutral state. The development of a transmission that can be realized is awaited.

  The present invention relates to an improvement of a transmission for solving the above-described problems, and in particular, adjustment of a feeling of load moderation by engaging a stopper member with a cam recess corresponding to a neutral shift position of a cam provided on one side of a shift drum. The shift drum is driven intermittently, the stopper member is pressed against a cam provided integrally with the shift drum, the shift position is positioned, and a plurality of shift shift stages are provided. In the transmission configured to switch the neutral state, a load generator for applying an auxiliary stopping force to the shift drum so that the shift drum stops in the neutral state when the shift drum is positioned in the neutral state is provided. It is characterized by that.

Further, the auxiliary stopping force in the load generating device is applied to a second cam that restricts the rotation of the shift drum provided separately from the cam.
Further, the auxiliary stopping force in the load generating device is generated by an attractive force of a magnetic body and a magnet provided on the shift drum.

Further, the application of the auxiliary stopping force by the load generating device is performed via a pressing element, the load generating device includes auxiliary force generating means for applying a predetermined auxiliary force in the application direction to the pressing element, and the pressing element And a means for allowing displacement toward the auxiliary force generating means opposite to the application direction.
Further, the second cam is formed by a combination of a concave portion provided on a side surface of the shift drum and an application portion ball of the load generating device to be fitted therewith.
Further, the auxiliary force generating means is an electromagnet.

  According to the first aspect of the present invention, in the transmission, when the shift drum is positioned in the neutral state, a load is generated to apply an auxiliary stop force to the shift drum so that the shift drum stops in the neutral state. Since the device is provided, it is possible to improve the reliability of the gear switching operation between the two gears across the neutral shift position. Further, by increasing the sense of moderation at the neutral shift position in the intermittent drive of the shift drum, the neutral shift position can be easily obtained, that is, switching to the neutral state is facilitated, and operability in shifting is improved.

  According to a second aspect of the present invention, in the transmission according to the first aspect, the application of the auxiliary stopping force in the load generating device regulates the rotation of the shift drum provided separately from the cam. Since it is made with respect to the second cam, the stop of the shift drum at the neutral shift position can be reliably and stably held, and the moderation feeling at the neutral shift corresponding position in the intermittent drive of the shift drum can be easily increased. Thus, it is possible to improve the reliability of switching of the transmission gear and the operability thereof.

  According to a third aspect of the present invention, in the transmission according to the first aspect, since the auxiliary stopping force in the load generating device is generated by the attraction force between the magnetic body and the magnet provided on the shift drum, According to the structure, an appropriate rotational load force can be applied at the neutral shift corresponding position in the intermittent drive of the shift drum, the moderation feeling can be enhanced, and the operability of the shift can be improved.

  According to a fourth aspect of the present invention, in the transmission according to the first or second aspect, the auxiliary stop force is applied by the load generating device via a pressing element, and the load generating device is Since there is provided auxiliary force generating means for applying a predetermined auxiliary force in the application direction to the pressing element, and means for allowing displacement of the pressing element toward the auxiliary force generating means opposite to the application direction. It is possible to apply an appropriate rotational resistance load force at the position corresponding to the neutral shift in the rotation of the.

  In addition, it is possible to secure a stable holding force at the position corresponding to the neutral shift, and it is possible to obtain an appropriate moderation feeling at the position corresponding to the neutral shift in the intermittent drive of the shift drum. Improvements can be made.

  Further, according to a fifth aspect of the present invention, in the transmission according to the second aspect, the second cam is a recess provided on a side surface of the shift drum and an application portion of the load generating device mated therewith. Due to the combination with the ball, it is possible to obtain a stable holding force at the position corresponding to the neutral shift and an appropriate moderation feeling at the position corresponding to the neutral shift in the intermittent drive of the shift drum by a simple structure.

  Further, according to a sixth aspect of the present invention, in the transmission according to the fourth aspect, since the auxiliary force generating means is an electromagnet, the auxiliary force can be adjusted by controlling an energization amount to the electromagnet. In addition, it is possible to easily adjust the moderation feeling at the position corresponding to the neutral shift in the intermittent drive of the shift drum by simple means, and it is easy to adjust the holding force at the corresponding position.

  An embodiment of the present invention will be described with reference to FIGS.

  As shown in FIG. 1, the shift drum 4 includes a shaft body 4b having a middle portion 4a having a middle thickness, the middle thickness portion of the middle portion 4a is hollow, and both end portions are narrow. The projecting shaft portions 4c and 4d are the left shaft portion 4c of the projecting shaft portions 4c and 4d in FIG. 1, the shaft end 4c1 of which is a bearing support 4e, and the shaft end 4c1 is engaged with the shaft end 4c1. A member 41A, which is one of the operating force transmission members 41 to which the pin 41A1 is mounted, is fixed by a bolt B, and is positioned so as to face the transmission member 41A and engages with the pin 41A1 of the transmission member 41A A member 41B that is the other of the operating force transmission member 41 including the portion 41B1 is attached to an arm member 42 that is interlocked with a shift pedal (not shown).

Therefore, the rotation of the arm member 42 by the operation of a shift pedal (not shown) is transmitted from the other operation force transmission member 41B to the one operation force transmission member 41A through the engagement of the claw portion 41B1 and the engagement pin 41A1, As a result, the shift drum 4 is rotated.
Further, a cam plate 6 described later is attached to the outer shaft end 4d1 of the shaft portion 4d on the right side in the drawing of FIG. 1 among the projecting shaft portions 4c and 4d of the shift drum 4.

  On the outer peripheral surface 4f of the middle-thick hollow shaft body 4b of the center portion 4a of the shift drum 4, the above-described cam grooves 4g for moving the shifter 5 are formed, and these cam grooves 4g are formed on the outer peripheral surface. 4f extends obliquely, that is, with a predetermined depth so as to form a spiral on the outer peripheral surface 4f, and one shifter 5 is provided in each of the cam grooves 4g. The base groove sliding hole 5b is slidably fitted to one of a pair of shift fork shafts 51 and 52 arranged in parallel with the shift drum 4 and fitted to the cam groove 4g. On the other hand, it is arranged to be movable in the left-right direction.

  The shifters 5 fitted into the three cam grooves 4g, that is, the three shifters 5, respectively, have their bases fitted into the grooves 4g via the protruding guide pins 5a as described above, and The base sliding hole 5b is slidably fitted to and supported by one of the pair of shift fork shafts 51, 52. Two of the shifters 5 are connected to one shift fork shaft 51 and one shift fork shaft 51. Is fitted and supported by the other shift fork shaft 52.

  The two shifters 5 and 5 supported by one shift fork shaft 51 are used for movement of a predetermined transmission gear in a gear group mounted on a counter shaft (not shown) and 1 supported by the other shift fork shaft 52. The book shifter 5 is a shifter 5 that is used for movement of a predetermined transmission gear in a gear group mounted on a main shaft (not shown).

  Each shifter 5 is guided by the shift fork shaft 51 or 52 through its base sliding hole 5b and slides to the left and right for movement of a predetermined transmission gear in the above-described gear group. The tip of the shift gear is formed as a shift fork portion 5c bifurcated for the movement of the transmission gear, although not clearly shown in the figure.

  The bifurcated shift fork portion 5c is engaged across the circumferential groove so as to hold a part of the circumferential groove of the sleeve of the predetermined transmission gear of the gear group on the main shaft or counter shaft (not shown). The shift gear is slid right and left on the shaft through the gear sleeve as the shifter 5 is moved by the rotation of the shift drum 4 based on the shift operation.

  Therefore, as can be understood by referring to FIG. 1, in the shift by the shift drum 4, the rotation of the arm member 42 by a shift pedal operation (not shown) is transmitted to the shift drum 4, and the outer peripheral surface 4 f of the shift drum 4 is already described. The predetermined shifter 5 is guided by the shift fork shaft 51 or 52 through the cam groove 4g and moved in the left-right direction. Then, by the movement of the shifter 5, a predetermined transmission gear in a gear group (not shown) on the main shaft or counter shaft (not shown) with which the shift fork 5c at the tip of the shifter 5 is engaged is moved. A gear at a desired shift stage is selected by selecting the meshing of a set of gears.

  By the way, as described above, the cam plate 6 is fixed to the shaft end 4d1 of the protruding shaft portion 4d on the right side of the shift drum 4 shown in FIG. 1, and this cam plate 6 is shown in FIG. And a plate having a substantially star shape such as a flat steel plate or an aluminum alloy having a predetermined thickness, and one flat side surface of the plate is in contact with the shaft end 4d1 of the protruding shaft portion 4d and the central portion of the plate material By being tightened by the tightening bolt B through the opening 6c, the shaft end 4d1 is firmly fixed.

  As described above and as shown in FIG. 2B, the cam plate 6 has a substantially star-shaped outer shape, and has six convex shapes projecting at substantially equal intervals on the outer circumference. A cam portion formed by these concavo-convex portions 6a and 6b, each of which includes a portion 6a and six concave portions 6b which are cam concave portions which will be described later and are arranged between the convex portions 6a. The upper curve continuously forms the outer shape of the star-shaped cam plate 6 relatively smoothly.

  The concave-convex portions 6b of the concave-convex portions forming the outer periphery of the star-shaped cam plate 6 form cam concave portions 6b corresponding to shift shift position positions for shifting, and in this embodiment, so-called six-stages. Since the speed is changed, six cam recesses 6b1 to 6b6 are provided. The relationship between the cam recesses 6b1 to 6b6 of the cam plate 6 corresponding to each of these shift shift stages and the rotational position of the shift drum 4 is aligned with each other. Attachment to the 4d shaft end 4d1 is made in the alignment relationship.

  A stopper roller 7a is always pressed against the outer periphery of the star-shaped cam plate 6 attached to the shift drum 4 with a predetermined elastic contact force in the alignment relationship. The stopper roller 7a is press-engaged by the elastic contact force of the cam recess 6b on the outer periphery of the star cam plate 6 to hold the star cam plate 6 at a position corresponding to the shift position with a predetermined elastic contact force. The shift drum 4 integral with the mold cam plate 6 is held with a predetermined rotational resistance load force at the shift shift stage corresponding position.

  The mechanism 7 for pressing the pressing element (pressing member) which is the stopper roller 7a to the outer periphery of the star-shaped cam plate 6 as described above is a stopper mechanism including pressing means 7b for pressing the stopper roller 7a for the pressing. 7, the mechanism 7 includes a stopper roller 7 a as a pressing element, and supports the roller 7 a at a tip end portion 7 c in a predetermined play permitting state and a pressing means, ie, a lever, for elastic contact with the roller 7 a The base portion 7e provided with a spring 7d for applying the rotational force is composed of a swing lever 7f that is rotatably supported by a predetermined structure portion of the crankcase.

  The stopper roller 7a, which is a pressing element of the rocking lever 7f tip 7c, is supported at the tip 7c in a predetermined free movement state as described above. The support at the lever tip 7c of the roller 7a is supported at the tip. The shaft portion 7a1 of the stopper roller 7a is loosely fitted in the long hole 7g of the portion 7c, the leaf spring 7h is brought into contact with the outer peripheral portion of the roller 7a, and the roller 7a is urged toward the outer peripheral periphery of the cam plate 6. It is done by doing.

  The stopper roller 7a is provided with a protruding step 7i having a gentle arc shape protruding toward the center of the roller 7a in a side view of the roller 7a. Both ends reach the outer peripheral portion of the roller 7a, and one side edge 7j of the tip of the swing lever 7f abuts on the protruding step portion 7i, whereby the roller 7a supported by the tip portion 7c of the swing lever is supported. The play allowance range is limited.

  Then, the stopper roller 7a of the stopper mechanism 7 is inserted into one of the cam recesses 6b1 to 6b6 of the cam plate 6 corresponding to the rotation stop position of the shift drum 4 in the selection of a desired shift shift stage through operation of a shift pedal (not shown). As described above, the predetermined rotational resistance load force is applied to the shift drum 4 via the cam plate 6 and the desired shift shift position is maintained.

  For example, the shift drum 4 is rotated in the direction A (indicated by the dotted line) in FIG. 2B in the speed change for increasing the speed. The selection of the cam recesses 6b1 to 6b6 corresponding to each selected shift shift stage in the star-shaped cam plate 6 that is shifted from the first speed to the sixth speed and rotates together with the drum 4 is also performed sequentially from the first speed to the sixth speed. Then, press contact engagement is made by the stopper roller 7a in the selection cam recess 6b, and the shift drum 4 is held under a predetermined rotational resistance load force at the selected shift shift stage.

  In this embodiment, the convex portion 6a1 between the cam recesses 6b1 and 6b2 corresponding to the first speed and the second speed of the star-shaped cam plate 6 is positioned as a neutral corresponding portion. The shape portion 6a1 has a cam recess 6b7 corresponding to a neutral shift for press-engaging the stopper roller 7a at the tip thereof, and the star-shaped cam plate 6 is interposed by press-engaging the stopper roller 7a to the cam recess 6b7. Thus, the shift drum 4 is held in a neutral state between the first and second speed shift stages with a predetermined rotational resistance load force.

  As shown in FIG. 2 (a), the star cam plate 6 is located concentrically with the star cam plate 6 adjacent to the outer side of the star cam plate 6 attached to the left protruding shaft end 4d1 of the shift drum 4. A neutral cam plate 8 is provided as a second cam plate. The neutral cam plate 8 is mounted using mounting bolts B provided for mounting the star cam plate 6 to the protruding shaft shaft end 4d1. The hexagonal head of the mounting bolt B is fitted and fixed in a fitting hole 8b formed in the center of the plate 8, and this fitting and fixing is usually fixed by press-fitting. At that time, application of an adhesive or the like to the press-fitting surface is performed, and combined use of means such as press-fitting and welding is also an appropriate option.

  The neutral cam plate 8 has a disk-like outer shape having a predetermined thickness, and a metal plate such as aluminum or a synthetic resin material is appropriately used as a suitable material. The V-shaped cam groove 8a is a cam groove 8a used corresponding to the neutral shift position of the shift drum 4, and the shift drum 4 is shifted to the neutral shift position. When this occurs, a stopper roller 9a, which is a pressing element (pressing member) of the second stopper mechanism 9 disposed corresponding to the neutral cam plate 8, engages with the cam groove 8a, and the shift drum 4 A predetermined rotational resistance load force is applied via the cam plate 8.

  Accordingly, the stopper operation of the shift drum 4 at the neutral shift position is substantially the same as the pressure contact engagement by the stopper roller 7a of the first stopper mechanism 7 to the neutral shift-compatible cam recess 6b7 in the star-shaped cam plate 6. The rotational cam load 8 is applied to the V-shaped cam groove 8a of the neutral cam plate 8 by applying a rotational resistance load force by the press contact engagement of the stopper mechanism 9 of the second stopper mechanism 9 by the stopper roller 9a. The neutral shift position of the shift drum 4 on which the stopper mechanisms 7 and 9 on the stage act are stably held with a large holding force, and a great moderation feeling is given at the neutral shift position by the intermittent drive of the shift drum 4 in the shift pedal operation. It is what

  Various modes of press-contact engagement by the stopper mechanism 9 by the neutral cam plate 8 exist. In the mode illustrated in FIG. 2 (hereinafter referred to as mode 1), the stopper mechanism corresponding to the neutral cam plate 8 is shown. 9, a link mechanism 9b is used as a load applying portion of a load generating device (roller pressing means) of the stopper mechanism 9.

  The load generating device as roller pressing means of the stopper mechanism 9 includes a cylindrical cylinder 9c and a flange 9f loosely fitted in the cylinder 9c at one shaft end 9e thereof, and the other cylinder 9c extending outwardly. A shaft member 9d having a stopper roller 9a that is rotatably supported at the end 9g; a piston 9i that slides within the cylinder 9c and that has a shaft portion 9h extending outside the cylinder 9c and coupled to the link mechanism 9b; Furthermore, a spring member 9j that associates these constituent members in an elastic mechanism is provided.

  The spring member 9j has one spring member 9j1 disposed between the inner side of one end forming portion of the cylinder 9c and one surface of the flange 9f of the shaft member 9d, and the other spring member 9j2 is disposed on the piston 9i. Between one side of the flange and the other side of the flange 9f. Therefore, the shaft member 9d has a flange 9f sandwiched between the two springs 9j1 and 9j2 in the cylinder 9c on both sides thereof, and is loosely fitted and held so that the amount of movement in and out of the cylinder 9c is variable. It is supported.

  2B, when the initial pressing force Fo in the direction of arrow Z is applied to one end of the link mechanism 9b, the link member-connected piston 9i of the link mechanism 9b slides down in the cylinder 9c. Then, the second spring 9j2 is compressed, but at the same time, the first spring 9j1 is compressed via the flange 9f, and the shaft member 9d integrated with the flange 9f is moved downward.

  By the downward movement of the shaft member 9d, the stopper roller 9a rotatably attached to the tip of the shaft member 9d is pushed into the V-shaped cam groove 8a of the neutral cam plate 8, and into the cam groove 8a by the roller 9a. The pressure contact force is increased. And if the desired pressing force F of the cam groove 8a press-contact by the stopper roller 9a is obtained, the pressing force provided to the said one end of the link mechanism 9b will be hold | maintained as it is.

  Therefore, a means for applying the pressing force and holding the pressing force is provided at the one end, which is the pressing force applying end of the link mechanism 9b, and the means for that purpose is a means that is conventionally used as appropriate. Although not shown in the drawings, for example, a string or wire attached to the link end by adjusting the pressing force F by adjusting the bolt screwing amount of the adjusting screw mechanism and holding the screwing amount of the bolt that has been press adjusted. It may be a means for adjusting the pressing force F by adjusting the winding of the wire and holding the string or wire adjusted for winding.

  The adjustment of the pressing force F can be controlled based on the detection of the position corresponding to the neutral shift in the rotation of the shift drum 4, and the neutral shift is performed by operating a pressing force adjusting mechanism (not shown) based on the detection signal based on this detection. For example, when the rotational position of the shift drum 4 reaches the neutral shift position or the vicinity of the shift position by adjusting the pressing force in the position or in the vicinity of the shift position, it is applied to the link end through the operation of the pressing adjustment mechanism. It is possible to perform control such as increasing the pressing force to be generated or generating an initial pressing force at the link end.

  With this control, it is possible to adjust the moderation feeling at the neutral shift position in the rotation of the shift drum 4 by operating the shift pedal (not shown), and it is easy to obtain the neutral shift position, that is, easy switching to the neutral state. And the holding force can be adjusted appropriately at the neutral shift position. As the pressure adjusting mechanism, a small motor or the like that is operated in response to a detection signal is appropriately employed.

  Further, in this stopper mechanism 9, a link mechanism 9b which is a pressing force applying member of a load generating device which is a roller pressing means for pressing and engaging the stopper roller 9a with the V-shaped cam groove 8a of the cam plate 8 is provided. Instead, a hydraulically actuated pressing force applying member can be employed, and in the hydraulic operation, the force of applying the pressing action of the piston 9i by the link mechanism 9b is replaced with the pressing action applying force of the piston 9i by a known hydraulic mechanism. Achieved. Adoption of a hydraulic mechanism can improve controllability by controlling the valve.

  In another aspect 2 shown in FIG. 3, the stopper mechanism 91 is a load generating device (roller pressing means) for press-fitting engagement of the stopper roller 91a with the V-shaped cam groove 81a of the neutral cam plate 81. An electromagnet 91b is used.

  The load generating device of the stopper mechanism 91 includes a cylindrical cylinder 91c and a flange 91f that is loosely fitted in the cylinder 91c at one of its shaft ends, and the other extends outside the cylinder 91c and has its shaft end. A shaft member 91d provided with a stopper roller 91a that is rotatably supported on the shaft 91, a spring member 91j disposed between the inner surface of one end forming portion of the cylinder 91c and one surface of the flange 91f of the shaft member 91d, and the flange The permanent magnet 91g disposed on the other surface of 91f, and the permanent magnet 91g, which is positioned so as to face the permanent magnet 91g with a predetermined gap, and is disposed at the other end of the cylinder 91c. Electromagnet 91b.

  Therefore, in the illustration of FIG. 3, when the electromagnet 91b is not energized, the shaft member 91d provided with the stopper roller 91a at the other axial end is pushed upward by the spring member 91j via the one end flange 91f. The stopper roller 91a is held in a state in which the pressure contact force of the neutral cam plate 81 to the V-shaped cam groove 81a is released.

  On the other hand, when the electromagnet 91b is energized, a repulsive force is generated between the electromagnet 91b and the permanent magnet 91g on the surface of the flange 91f so that the magnetic poles have the same polarity, thereby causing the flange 91f to resist the spring member 91j. The spring member 91j is moved downward while compressing the spring member 91j, and the stopper roller 91a is brought into pressure contact with the V-shaped cam groove 81a of the neutral cam plate 81 with a predetermined pressing force (elastic force) F. it can. The pressure contact force F is adjusted by adjusting the energization amount to the electromagnet 91b, and the holding state by the predetermined pressing force F is easily made by maintaining the predetermined energization amount to the electromagnet 91b.

  Also in this aspect 2, control of the pressing force to the neutral cam plate 81 by the stopper mechanism 91 at or near the neutral shift corresponding position based on detection of the neutral shift corresponding position in the rotation of the shift drum 4 is performed. This control is performed by energization control to the electromagnet 91b based on a detection signal based on detection of a neutral shift-corresponding position in the rotation of the shift drum 4, whereby the neutral in rotation of the shift drum 4 by operation of a shift pedal (not shown). It is possible to adjust the degree of moderation and adjust the holding power at the shift corresponding position.

  By the way, in the modes 1 and 2 shown in FIGS. 2 and 3, the neutral cam plates 8 and 81 are provided with V-shaped cam grooves 8a and 81a corresponding to the neutral shift position on the outer periphery thereof. In place of the neutral cam plates 8 and 81, in the mode 3 shown in FIG. 4, a neutral cam plate 82 of another type is used, and the cam plate 82 is located near the outer periphery of the outer surface 82b. The concave portion 82a is formed as a cam concave portion 82a that is used for press contact with the pressing element corresponding to the neutral shift position.

  Therefore, the structure of the stopper mechanism 92 disposed corresponding to the cam plate 82 is changed with the use of the neutral cam plate 82, and the stopper mechanism 92 is press-engaged with the cam recess 82a. The stopper ball 92a has a spherical pressing element, and the press contact engagement of the stopper ball 92a at the position corresponding to the neutral shift of the cam plate 82 causes the stopper ball 92a to move from the direction of the outer surface 82b of the neutral cam plate 82. This is done by being pushed by the stopper mechanism 92 and being pressed against the cam recess 82a on the side surface 82b.

  A load generating device (ball pressing means) for pressing the spherical stopper ball 92a, which is a pressing element in the stopper mechanism 92, into the cam recess 82a is a stopper that is a pressing element of the stopper mechanism 9 in the above-described aspect 1. A device that is substantially the same as the load generating device for pressing the roller 9a is used.

  That is, a cylinder 92c and a flange 92f loosely fitted in the cylinder 92c are provided at one shaft end of the shaft portion located in the cylinder 92c, and a stopper is provided at the other shaft end of the shaft portion extending outside the cylinder 92c. A shaft member 92d having a ball 92a, a piston 92i that slides in the cylinder 92c and whose shaft portion 92h extends outside the cylinder 92c and is connected to the link mechanism 92b, and a spring member 92j that links these members in an elastic mechanism. One of the spring members 92j is disposed between one end forming portion of the cylinder 92c and one surface of the flange 92f of the shaft member 92d, and the other one 92j2 is disposed on the flange 92f. A load generator having a structure disposed between the other surface and one surface of the piston 92i is used.

  Therefore, the piston 92i is pushed into the cylinder 92c by the link member 92b with the addition of the initial pressing force Fo in the arrow direction Z in the link mechanism 92b shown in FIG. 4, and the second spring member 92j2 is compressed. The shaft member 92d operates to compress the first spring member 92j1 through the shaft end flange 92f and push the stopper ball 92a at the other shaft end into the cam recess 82a of the outer surface 82b of the neutral cam plate 82, The stopper ball 92a is brought into pressure contact with the cam recess 82a with a predetermined elastic force F.

  That is, the stopper ball 92a is pushed into the neutral cam plate 82 at the neutral compatible position from the side of the cam plate 82. The load generating device for the stopper mechanism 92 in this aspect 3 is as follows. There is substantially no difference in structure and operation from the load generating device of the stopper mechanism 9 in the above-described aspect 1. And in this aspect 3, it can replace with the link mechanism 92b which applies the initial stage pushing force Fo to the piston 92i in the stopper mechanism 92, and the hydraulic mechanism described in the above-mentioned aspect 1 can be used.

  In addition, what is shown as another embodiment 4 in FIG. 5 uses a cam plate 83 having the same structure as the cam plate 82 in which the pressing element in the third embodiment is pushed from the side as the neutral cam plate. A spherical stopper ball 93a is used as a pressing element that press-engages with the cam recess 83a of the cam plate 83, and a load generating device (ball pressing means) in the stopper mechanism 93 for press-engaging the stopper ball 93a. ) Is an embodiment in which a device substantially the same as the load generating device in the electromagnet-based stopper mechanism 91 used in the second mode is used, and means using an electromagnet 93b is employed.

  FIG. 6 shows still another embodiment 5 in which a neutral cam plate having a different structure is used. The neutral cam plate 84 includes the above-described neutral cam plates 8, 81, 82, It is slightly thinner than 83 and is made of a non-magnetic disc-shaped plate, and its central portion is fitted and fixed integrally with the hexagonal head of the star cam mounting bolt B, and its outer surface 84b. A member 84a made of a cylindrical magnetic body is fixed at one position near the outer periphery of the outer plate 84b so as to protrude a predetermined amount from the surface of the outer plate 84b.

  An electromagnet 94b is arranged so as to be able to ensure the opposing arrangement with the magnetic member 84a on the cam plate 84 in the rotation of the neutral cam plate 84. That is, the cam plate The electromagnet 94b is positioned and arranged so that it can take a position facing the member 84a made of a magnetic material on the cam plate 84 when the position 84 is set to the neutral shift corresponding position. It is attached to a predetermined structure portion of the crankcase with an arrangement position.

  Therefore, at the position corresponding to the neutral shift of the shift drum 4, the electromagnet 94b is opposed to the magnetic member 84a on the neutral cam plate 84 to constitute the load generating device of the stopper mechanism 94, and the electromagnet of this load generating device. The shift drum 4 is applied with a predetermined rotational resistance load force through the cam plate 84 by the adsorption action of 94b and is held at the neutral shift position. Further, when the electromagnet 94b is energized, a shift in shift pedal operation for shifting is performed. A moderation feeling at the neutral shift position due to the rotation of the drum 4 can be obtained. The moderation feeling and the holding strength can be adjusted by controlling the amount of current supplied to the electromagnet 94b.

  Also in this aspect 5, the neutral shift position based on the detection of the neutral shift corresponding position in the rotation of the shift drum 4 or the pressing force to the neutral cam plate 84 by the stopper mechanism 94 near the shift position, that is, the electromagnet 94d. The cam attracting force can be controlled by the control by the energization control of the electromagnet 94d by receiving the detection signal based on the detection, whereby the neutral due to the rotation of the shift drum 5 in the shift pedal operation (not shown). It is possible to adjust the degree of moderation at the shift position and the holding power.

  Since the transmission according to the present invention has the above-described configuration, the following effects can be obtained.

  A neutral cam plate (8, 8) having a star-shaped cam plate 6 provided on one side of the shift drum 4 and a stopper portion that can adjust the pressure contact engagement force corresponding to the neutral shift position, which is separate from the cam plate 6. 81, 82, 83, and 84), and by adjusting the strength of the pressure contact engagement force by the stopper portion at the neutral shift position of the cam plate, an appropriate moderation feeling at the neutral position can be obtained in the intermittent drive of the shift pedal operation. Therefore, the neutral shift position can be easily obtained, that is, the ease of switching operation to the neutral state can be improved.

  In the stopper mechanism (9, 91, 92, 93, 94) respectively corresponding to the neutral cam plate (8, 81, 82, 83, 84), a stopper roller (9a, 91a) or a stopper ball as a pressing element. (92a, 93a) or the like can adjust the pressure contact force to the cam plate as appropriate, and can adjust the degree of moderation at the neutral shift position. Therefore, the pressure contact force to the cam plate by the pressing element is appropriately set. As a result, it is possible to ensure the switching of the gears in both gear shift stages, for example, the first and second speed shift stages with the neutral shift position interposed therebetween, and to improve the operability in the shift operation. .

  The position corresponding to the neutral shift is detected based on the rotation of the shift drum 4, and the pressing force of the stopper mechanism to the neutral cam plate is controlled by this detection signal. Therefore, the position corresponding to the neutral shift in the rotation of the shift drum 4 or the shift Fine control of the pressing force in the vicinity of the corresponding position becomes possible, and it becomes possible to set an optimum moderation feeling at the neutral shift position by the rotation of the shift drum 4 in the shift pedal operation, so that the neutral shift position can be easily obtained. That is, the ease of switching to the neutral state is improved. In addition, it is possible to set an appropriate holding force at the neutral shift position.

  In the stopper mechanisms (9, 91, 92, 93, 94) respectively corresponding to the neutral cam plates, load generating devices for pressing the pressing elements against the cam plates (8, 81, 82, 83, 84) (Pressing element pressing means) is a very simple mechanism that uses a link member or a spring member as its basic structure, or uses a magnet, an electromagnet, and a hydraulic mechanism. The operation of the load generator is simple, reliable and inexpensive.

It is the enlarged view made into the partial cross section which shows the principal part of the structure of this invention. It is a figure which shows the 1st aspect of the stopper mechanism of the neutral cam board of this invention. It is a figure which shows the 2nd aspect of the stopper mechanism of the neutral cam board of this invention. It is a figure which shows the 3rd aspect of the stopper mechanism of the neutral cam board of this invention. It is a figure which shows the 4th aspect of the stopper mechanism of the neutral cam board of this invention. It is a figure which shows the 5th aspect of the stopper mechanism of the neutral cam board of this invention.

Explanation of symbols

4 ... shift drum, 5 ... shifter, 51, 52 ... shifter fork shaft, 6 ... star cam plate, 6a ... convex portion, 6b, 6b1-6b7 ... cam recess (Concave part), 7 ... stopper mechanism, 7a ... stopper roller, 7f ... swing lever, 8, 81, 82, 83, 84 ... neutral cam plate, 8a, 81a ... Cam groove, 82a, 83a ... cam recess, 84a ... member made of magnetic material, 9, 91, 92, 93, 94 ... stopper mechanism, 9a, 91a ... stopper roller, 9b, 92b ..Link mechanism, 92a, 93a, stopper balls, 91b, 93b, 94b, electromagnet, 91g, permanent magnet.

Claims (6)

  1. In a transmission that intermittently drives a shift drum, presses a stopper member against a cam provided integrally with the shift drum, positions a shift position, and switches between a plurality of shift shift stages and a neutral state. A transmission comprising a load generator for applying an auxiliary stopping force to the shift drum so that the shift drum stops in the neutral state when the shift drum is positioned in the neutral state.
  2. 2. The transmission according to claim 1, wherein the application of the auxiliary stopping force in the load generating device is performed on a second cam that restricts rotation of the shift drum provided separately from the cam. .
  3. 2. The transmission according to claim 1, wherein the auxiliary stopping force in the load generating device is generated by an attractive force of a magnetic body and a magnet provided on the shift drum.
  4. The application of the auxiliary stopping force by the load generating device is performed via a pressing element, the load generating device applies auxiliary force generating means for applying a predetermined auxiliary force in the applying direction to the pressing element, and the application direction of the pressing element. The transmission according to claim 1 or 2, further comprising means for allowing displacement toward the auxiliary force generating means opposite to the first.
  5. 3. The transmission according to claim 2, wherein the second cam is composed of a combination of a recess provided on a side surface of the shift drum and an application part ball of the load generator to be fitted therewith.
  6. 5. The transmission according to claim 4, wherein the auxiliary force generating means is an electromagnet.
JP2004275768A 2004-09-22 2004-09-22 Gear shifter Pending JP2006090405A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2004275768A JP2006090405A (en) 2004-09-22 2004-09-22 Gear shifter

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004275768A JP2006090405A (en) 2004-09-22 2004-09-22 Gear shifter

Publications (1)

Publication Number Publication Date
JP2006090405A true JP2006090405A (en) 2006-04-06

Family

ID=36231582

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2004275768A Pending JP2006090405A (en) 2004-09-22 2004-09-22 Gear shifter

Country Status (1)

Country Link
JP (1) JP2006090405A (en)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008215555A (en) * 2007-03-06 2008-09-18 Honda Motor Co Ltd Automatic transmission
JP2008215554A (en) * 2007-03-06 2008-09-18 Honda Motor Co Ltd Automatic transmission
JP2010054001A (en) * 2008-08-29 2010-03-11 Honda Motor Co Ltd Transmission of vehicle
JP2011196433A (en) * 2010-03-18 2011-10-06 Honda Motor Co Ltd Shift control device of saddle-riding type vehicle
WO2012152445A1 (en) * 2011-05-11 2012-11-15 Audi Ag Shifting device
CN102889377A (en) * 2011-07-20 2013-01-23 C.R.F.阿西安尼顾问公司 Gear change device for a motor vehicle
CN108138952A (en) * 2016-02-08 2018-06-08 宝马股份公司 For the device and method of the gearshift drum of locking list type speed changer

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS49103144U (en) * 1972-12-27 1974-09-04
US6487927B1 (en) * 1999-08-23 2002-12-03 Alan C. Sputhe Automatic neutral finder for a motorcycle transmission

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS49103144U (en) * 1972-12-27 1974-09-04
US6487927B1 (en) * 1999-08-23 2002-12-03 Alan C. Sputhe Automatic neutral finder for a motorcycle transmission

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008215555A (en) * 2007-03-06 2008-09-18 Honda Motor Co Ltd Automatic transmission
JP2008215554A (en) * 2007-03-06 2008-09-18 Honda Motor Co Ltd Automatic transmission
JP2010054001A (en) * 2008-08-29 2010-03-11 Honda Motor Co Ltd Transmission of vehicle
JP2011196433A (en) * 2010-03-18 2011-10-06 Honda Motor Co Ltd Shift control device of saddle-riding type vehicle
WO2012152445A1 (en) * 2011-05-11 2012-11-15 Audi Ag Shifting device
CN102889377A (en) * 2011-07-20 2013-01-23 C.R.F.阿西安尼顾问公司 Gear change device for a motor vehicle
CN102889377B (en) * 2011-07-20 2015-05-06 C.R.F.阿西安尼顾问公司 Gear change device for a motor vehicle
CN108138952A (en) * 2016-02-08 2018-06-08 宝马股份公司 For the device and method of the gearshift drum of locking list type speed changer

Similar Documents

Publication Publication Date Title
US9739322B2 (en) Electric actuator module for selectable clutch
JP5514196B2 (en) Operating device with force feedback
CN102105715B (en) Compact selection mechanism for a selectable one-way clutch
US7752936B2 (en) Automatic transmission assembly for a vehicle, and vehicle incorporating same
JP3321045B2 (en) Bicycle electrical operating device
EP2098758B1 (en) Shifter for vehicle transmission
US8607657B2 (en) Actuation device with haptic emulation
US6405611B1 (en) Electrical sensing system for a vehicle shifter
DE102007006354B4 (en) Parking lock assembly for an electric transmission range selection system
KR101251503B1 (en) Shifting apparatus for manual transmission
JP4122012B2 (en) Bicycle electric shift control device
DE60204396T2 (en) Shift actuator for transmission
US7845247B2 (en) Shift fork actuation system for control of synchronizer position
JP4530779B2 (en) Shift position detection device for vehicle transmission
US6634249B2 (en) Shift actuator for a transmission
AU2006332253B2 (en) Clutch module for prostheses
US8011489B2 (en) Straddle-type vehicle
JP5981567B2 (en) Electro-hydraulic servo valve
KR20090010085A (en) Under travel actuator, particularly for an automobile clutch
JP4036424B2 (en) Manual transmission change device
DE60225629T2 (en) Transmission shifting device
US6932739B2 (en) Continuously variable transmission apparatus
EP1406033B1 (en) Electromagnetic solenoid and shift actuator for a transmission using the same
JP2011251667A (en) Gas pedal device
US20050022765A1 (en) Variable valve timing controller

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20061129

RD04 Notification of resignation of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7424

Effective date: 20090428

A977 Report on retrieval

Effective date: 20091126

Free format text: JAPANESE INTERMEDIATE CODE: A971007

A131 Notification of reasons for refusal

Effective date: 20091201

Free format text: JAPANESE INTERMEDIATE CODE: A131

A02 Decision of refusal

Effective date: 20100330

Free format text: JAPANESE INTERMEDIATE CODE: A02