JP2009074638A - Transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transmission capable of transmitting driving force not only in acceleration but also in deceleration when necessary, and capable of minimizing reduction in transmission efficiency by friction. <P>SOLUTION: This transmission can transmit the driving force in both acceleration and deceleration by being put in an engaging state of forcibly projecting a first engaging surface 71b of a strut 71 in a cutout 72 of a gear 21, and can also release the transmission of the driving force in deceleration by transmitting the driving force in acceleration, by being put in a one-way state of engaging or releasing engagement of the first engaging surface 71b of the strut 71 and a cutout 72 of a rotary shaft 12 in response to the relative rotational direction to the rotary shaft 12 of the gear 21, and can also cut off the transmission of the driving force in both acceleration and deceleration by being put in an unengaged state of forcibly retreating the first engaging surface 71b of the strut 71 from the cutout 72 of the gear 21, and moreover, can prevent reduction in the transmission efficiency when the friction is generated between the strut 71 and the gear 21. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention supports a plurality of gears on a rotating shaft so as to be relatively rotatable, and selectively couples any of the plurality of gears to the rotating shaft via a corresponding clutch mechanism, thereby achieving a desired shift speed. The present invention relates to an established transmission.

  In a bicycle transmission having three transmission shafts arranged in parallel, a plurality of gears corresponding to each gear stage fixed to the second transmission shaft arranged in the center, and first gears arranged on both sides of the second transmission shaft. 1. A plurality of gears corresponding to the respective speeds supported relatively rotatably on the third speed change shaft are meshed with each other, and the first and third speed change shafts formed hollow and the gears supported on the outer periphery thereof are formed. A ratchet one-way mechanism or a ball one-way mechanism is disposed between them, and a clutch operator disposed inside the first and third transmission shafts is moved in the axial direction to selectively activate the one-way mechanism. Japanese Patent Application Laid-Open Publication No. 2004-151867 discloses that a gear is selectively coupled to first and third transmission shafts to establish a desired gear position.

A drive gear fixed to the input shaft and a driven gear supported relatively rotatably on the output shaft are meshed with each other, and a steel ball stored in a storage hole penetrating the output shaft in the radial direction is placed inside the input shaft. By moving the shaft in the radial direction with a shift lever arranged so as to be movable in the axial direction and engaging with a fitting groove formed on the inner peripheral surface of the driven gear, one of the driven gears is coupled to the output shaft to achieve a desired speed change. The one that establishes a stage is known from US Pat.
Japanese Patent No. 3838494 Japanese Utility Model Publication No. 61-39871

  However, the one described in the above-mentioned patent document 1 is that when the one-way mechanism of the gear of the established gear stage is engaged, the one-way mechanism of the other gear stage is slipping, so that the slip of the one-way mechanism is There is a problem that the transmission efficiency decreases due to the friction caused by the friction. Moreover, because the one-way mechanism can always slip, it can be used when the driving force is transmitted only during acceleration and not when decelerating, such as a bicycle. For this reason, there is a problem that it is impossible to use a device that needs to transmit driving force even during deceleration.

  In addition, since the driving force is transmitted through the steel ball by point contact, the one described in Patent Document 2 not only has the possibility of causing wear and deformation on the surface of the steel ball, but also the slip of the one-way mechanism. Even when the steel ball is pressed against the inner peripheral surface of the driven gear by centrifugal force, there is a problem that friction acts between the steel ball and the driven gear to reduce transmission efficiency.

  The present invention has been made in view of the above circumstances, and can transmit a driving force not only during acceleration but also when decelerating as necessary, and can minimize a decrease in transmission efficiency due to friction. An object is to provide a transmission.

  In order to achieve the above object, according to the first aspect of the present invention, a plurality of gears are rotatably supported on a rotating shaft, and any one of the plurality of gears is connected via a corresponding clutch mechanism. In the transmission capable of establishing a desired shift speed by being selectively coupled to the rotating shaft, the clutch mechanism includes a strut housing groove provided on an outer peripheral portion of the rotating shaft formed in a hollow shape, A strut that is swingably supported in the strut housing groove, and a first engagement surface that is provided on the gear rotation direction delay side of the strut and is engageable with a notch formed on the inner peripheral surface of the gear. And a second engagement surface that is provided on the gear rotation direction advance side of the strut and engages with the strut accommodation groove, and is disposed inside the rotation shaft so as to be movable in the axial direction. Slurry to control the state Depending on the position of the cam, the strut first engagement surface is forcibly projected into the notch of the gear, and the relative rotation direction of the gear with respect to the rotation shaft, A one-way state in which the first engaging surface of the strut and the notch of the rotating shaft are engaged or disengaged, and the non-engagement for forcibly retracting the first engaging surface of the strut from the notch of the gear. A transmission is proposed which is characterized in that it can be switched between the combined states.

  According to the second aspect of the present invention, in addition to the configuration of the first aspect, the clutch mechanism communicates with the gear rotation direction delay side of the strut housing groove and penetrates the rotation shaft in the radial direction. A headball housing hole, a headball that is fitted in the headball housing hole so as to be movable in a radial direction, and that can be brought into contact with a radially inner surface of the strut gear rotation direction delay side end, and a gear in the strut housing groove A tail ball storage hole that communicates with the rotation direction advance side and penetrates the rotation shaft in the radial direction, and is fitted to the tail ball storage hole so as to be movable in the radial direction, and the diameter of the strut gear rotation direction advance side end portion A tail ball capable of abutting on the inner surface in the direction, and the slide cam is capable of controlling a radial position of the head ball and the tail ball, and the tape is controlled according to the position of the slide cam. An engagement state in which the first engagement surface of the strut is forcibly protruded into the notch of the gear by pushing the head ball radially outward while allowing the ball to move radially inward. A one-way state in which the first engagement surface of the strut and the notch of the gear are engaged or disengaged by allowing the tail ball and the head ball to move radially inward. The non-engagement of forcing the first engagement surface of the strut to retract from the notch of the gear by pushing the tail ball radially outward while allowing the head ball to move radially inward. A transmission is proposed which is characterized in that it can be switched between the combined states.

  According to a third aspect of the present invention, in addition to the configuration of the second aspect, the first engaging surface of the strut and the notch of the gear are in surface contact during acceleration, and the strut first A transmission is proposed in which the two engaging surfaces are in surface contact with the strut receiving groove of the rotating shaft.

  According to the invention described in claim 4, in addition to the configuration of claim 2, the driving force at the time of deceleration in the engaged state is generated from the notch of the gear to the first engaging surface of the strut. A transmission is proposed which is transmitted to the rotary shaft through the headball and the headball storage hole.

  According to a fifth aspect of the invention, in addition to the configuration of the second aspect, during acceleration in the one-way state, the headball is urged to a radially outer position by its centrifugal force, and the engagement is performed. A transmission as claimed in claim 2 is proposed, characterized in that the combined state is maintained.

  According to the invention described in claim 6, in addition to the configuration of any one of claims 1 to 5, each of the gears has an axially opposite end portion of the rotary shaft via a pair of bearing members. A transmission is proposed in which the clutch mechanism is disposed in a space sandwiched between the pair of bearing members.

  According to a seventh aspect of the invention, in addition to the configuration of the sixth aspect, the bearing member simultaneously supports two adjacently arranged gears out of the plurality of gears. A transmission is proposed.

  According to the invention described in claim 8, in addition to the structure of any one of claims 2 to 5, the headball and the tailball are respectively stored in the headball storage hole and the tailball storage hole. In such a state, the struts are stored in the strut storage grooves so as to cover the outer sides in the radial direction, and set ring engaging portions protruding from both end surfaces in the axial direction of the struts are fitted to the outer periphery of the output shaft. A transmission characterized by being held on the inner peripheral surface of the set ring is proposed.

  The output shaft 12 of the embodiment corresponds to the rotating shaft of the present invention, the 1st to 7th speed driven gears 21 to 27 of the embodiment correspond to the gear of the present invention, and the bush 28 and ball bearing of the embodiment. 28 'corresponds to the bearing member of the present invention.

  According to the configuration of the first aspect, the clutch mechanism supports the strut in a strut housing groove provided in the outer peripheral portion of the hollow rotary shaft so as to be swingable, and the inner periphery of the gear on the delay side in the gear rotation direction of the strut. Since the first engagement surface that can be engaged with the notch provided on the surface is provided, and the second engagement surface that engages with the strut accommodation groove is provided on the strut gear rotation direction advance side, the rotation shaft is provided inside. By adjusting the axial position of the provided slide cam, the swinging state of the strut can be controlled to change the position of the first engagement surface. Therefore, the driving force can be transmitted both when accelerating and decelerating by forcing the first engaging surface of the strut to protrude into the gear notch. In addition, the driving force is transmitted during acceleration by adopting a one-way state in which the first engaging surface of the strut and the notch of the rotating shaft are engaged or released according to the relative rotation direction of the gear with respect to the rotating shaft. Thus, transmission of driving force can be canceled during deceleration. In addition, by disengaging the first engaging surface of the strut from the gear notch, the transmission of driving force can be cut off both during acceleration and deceleration, and the strut can be cut off. It is possible to prevent the transmission efficiency from being reduced due to friction between the gear and the gear.

  According to the second aspect of the present invention, the clutch mechanism communicates with the gear rotation direction delay side of the strut storage groove and passes through the rotation shaft in the radial direction, and is movable in the radial direction to the head ball storage hole. And a tail ball that is in contact with the radially inner surface of the strut gear rotation direction delay side end and communicates with the gear rotation direction advance side of the strut housing groove and penetrates the rotation shaft in the radial direction. The slide cam is provided with a storage hole and a tail ball that is fitted in the tail ball storage hole so as to be movable in the radial direction and can come into contact with the radial inner surface of the strut in the gear rotation direction advance side. By changing the position, the radial positions of the headball and tailball can be controlled. As a result, if the head ball is pushed radially outward while changing the position of the slide cam and allowing the tail ball to move radially inward, the first engaging surface of the strut is forced into the gear notch. The driving force can be transmitted both at the time of acceleration and at the time of deceleration as an engaged state that is projected in a normal manner. If the position of the slide cam is changed to allow both the tailball and the headball to move inward in the radial direction, the one-way that engages or disengages the first engaging surface of the strut and the gear notch. As a state, the driving force can be transmitted during acceleration and the transmission of the driving force during deceleration can be interrupted. In addition, if the tail ball is pushed radially outward while allowing the head ball to move radially inward by changing the position of the slide cam, the strut first engaging surface is forced from the gear notch. As the non-engaged state in which the vehicle is retracted, the transmission of the driving force can be interrupted both during acceleration and during deceleration.

  According to the third aspect of the present invention, the first engaging surface of the strut and the gear notch are in surface contact during acceleration, and the second engaging surface of the strut and the strut receiving groove of the rotating shaft are in surface contact during acceleration. Since the driving force is transmitted, the load at the time of acceleration with a large driving force can be transmitted by surface contact, and the wear and deformation of the struts due to the load transmission can be suppressed to increase durability.

  According to the fourth aspect of the present invention, the driving force is transmitted from the gear notch to the rotating shaft through the strut, the headball, and the headball storage hole during deceleration in the engaged state. In addition, the driving force can be transmitted during deceleration.

  According to the fifth aspect of the present invention, the headball is urged to the radially outer position by its centrifugal force during transmission in the one-way state to transmit the driving force. The one-way state can be established without being influenced by the above.

  According to the configuration of claim 6, both end portions in the axial direction of each gear are supported on the outer periphery of the rotating shaft via a pair of bearing members, and the clutch mechanism is arranged in a space sandwiched between the pair of bearing members. Therefore, the clutch mechanism can be arranged compactly while avoiding interference with the bearing member.

  According to the configuration of the seventh aspect, the bearing member simultaneously supports two adjacently arranged gears among the plurality of gears, so that the number of necessary bearing members can be minimized.

  Further, according to the configuration of claim 8, the radially outer sides of the headball and tailball respectively stored in the headball storage hole and the tailball storage hole are covered with the struts stored in the strut storage groove, and both ends of the strut in the axial direction are covered. Since the set ring engaging part protruding from the surface is held by the inner peripheral surface of the set ring that fits to the outer periphery of the output shaft, the set ball temporarily holds the headball, tail ball, and strut on the rotating shaft so that they cannot fall off. The assembly work can be facilitated.

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

  1 to 34 show a first embodiment of the present invention. FIG. 1 is a longitudinal sectional view of a transmission, FIG. 2 is an enlarged view of a part 2 in FIG. 1 (a sectional view taken along line 2-2 in FIG. 3). 3 is a sectional view taken along line 3-3 in FIG. 2, FIG. 4 is a sectional view taken along line 4-4 in FIG. 2, FIG. 5 is a sectional view taken along line 5-5 in FIG. 7 is an enlarged perspective view of part 7 of FIG. 6, FIG. 8 is a sectional view taken along line 8-8 in FIG. 6, FIG. 9 is a sectional view taken along line 9-9 in FIG. 11 is a sectional view taken along line 11-11 of FIG. 6, FIG. 12 is a sectional view taken along line 12-12 of FIG. 10, FIG. 13 is a perspective view of a slide cam and slider, and FIG. 14 is a strut, headball and tail. FIG. 15 is an operation explanatory view showing the engaged state of the driven gear, FIG. 16 is an operation explanatory view showing the one-way state of the driven gear, and FIG. 17 is an unengaged state of the driven gear. Use illustration, FIGS. 18 to 34 is an explanatory diagram of the operation of upshift and downshift.

  As shown in FIG. 1, for example, a forward seven-stage transmission T used in an F1 racing car includes a hollow input shaft 11 and a hollow output shaft 12 arranged in parallel with each other. An engine E is connected to one end side (hereinafter referred to as the left side), and an output gear 13 including a bevel gear is provided on the other end side (hereinafter referred to as the right side) of the output shaft 12 to transmit driving force to the drive wheels. From the right side to the left side of the input shaft 11, the first speed drive gear 14, the third speed drive gear 15, the fifth speed drive gear 16, the seventh speed drive gear 17, the second speed drive gear 18, the fourth speed drive gear 19th and 6th speed drive gear 20 is fixed. On the outer periphery of the output shaft 12, from the right side to the left side, the first speed driven gear 21, the third speed driven gear 22, the fifth speed driven gear 23, the seventh speed driven gear 24, and the second speed driven gear that are always meshed with the drive gears 14 to 20. 25, 4th speed driven gear 26 and 6th speed driven gear 27 are supported by bushes 28.

  An actuator shaft 29 fixed to a mission case (not shown) is coaxially arranged inside the output shaft 12, and a cylindrical cylinder 30 is supported on the outer periphery of the actuator shaft 29 so as to be movable in the axial direction. Further, a cylindrical slide cam 31 is supported on the outer periphery of the cylinder 30 via a pair of ball bearings 32 and 33 so as to be relatively rotatable and slidable in the axial direction. The slide cams 31 are arranged at equal intervals in the circumferential direction. The actuator springs 34 formed by a plurality of (8 in the embodiment) coil springs are floatingly supported so as to be movable relative to the cylinder 30 in the axial direction.

  When the cylinder 30 is moved from the right side to the left side of the output shaft 12 by the hydraulic pressure supplied from the inside of the actuator shaft 29, the slide cam 31 floatingly supported by the cylinder 30 via the actuator springs 34 is moved to the right side of the output shaft 12. To the left side, the first gear to the seventh gear are established in order. The transmission T cannot shift up or down by skipping the gear position.

  Next, the internal structure of the output shaft 12 will be described in more detail with reference to FIGS.

  As shown in FIG. 2, a stopper ring 41 and a collar 42 are fitted on the inner peripheral surface of the right end of the cylinder 30 fitted to the outer periphery of the actuator shaft 29 and fixed with a cap 43, and the collar 42 is fixed to the actuator shaft 29. A slide guide 44 and a seal member 45 are disposed on a portion that slides on the outer peripheral surface of the cylinder 30, a seal member 46 is disposed on a portion where the cap 43 slides on the outer peripheral surface of the actuator shaft 29, and the collar 42 is disposed on A seal member 47 is disposed in a portion that contacts the inner peripheral surface.

  A stopper ring 48, a collar 49, and a cap 50 are fitted to the inner circumferential surface of the left end of the cylinder 30 fitted to the outer circumference of the actuator shaft 29, and the cap 50 is fastened to the left end of the cylinder 30 with bolts 51. A slide guide 52 and a seal member 53 are disposed in a portion where the collar 49 slides on the outer peripheral surface of the actuator shaft 29, and a seal member 54 is disposed in a portion where the cap 50 slides on the outer peripheral surface of the actuator shaft 29. A seal member 55 is disposed at a portion where the collar 49 contacts the inner peripheral surface of the cylinder 30.

  A piston 29 a is formed at the intermediate portion of the actuator shaft 29, and a slide guide 56 and a seal member 57 that slide on the inner peripheral surface of the cylinder 30 are disposed on the piston 29 a. As a result, the first oil chamber 58 is defined between the piston 29a of the actuator shaft 29 and the collar 42 on the right end side of the cylinder 30, and between the piston 29a of the actuator shaft 29 and the collar 49 on the left end side of the cylinder 30. A second oil chamber 59 is defined. The first oil chamber 58 communicates with an oil pump or a reservoir (not shown) via a first oil passage 29 b formed inside the actuator shaft 29, and the second oil chamber 59 is a second oil chamber formed inside the actuator shaft 29. An oil pump or a reservoir (not shown) communicates with the passage 29c.

  Accordingly, when hydraulic pressure is supplied from the oil pump to the second oil chamber 59 via the second oil passage 29c, the hydraulic oil in the first oil chamber 58 is returned to the reservoir via the first oil passage 29b, thereby fixing the fixed actuator. When the cylinder 30 moves from the right side to the left side with respect to the shaft 29 and is shifted up, and hydraulic pressure is supplied from the oil pump to the first oil chamber 58 via the first oil passage 29b, the hydraulic oil in the second oil chamber 59 is supplied. Is returned to the reservoir through the second oil passage 29c, the cylinder 30 moves from the left side to the right side with respect to the fixed actuator shaft 29, and a downshift is performed.

  As described above, since the cylinder 30 which is a drive source for reciprocating the slide cam 31 in the axial direction is completely housed in the output shaft 12, the speed change can be achieved as compared with the case where the drive source is disposed outside the output shaft 12. The machine T can be reduced in size.

  As is apparent from FIGS. 2 and 3, eight actuator springs 34 are arranged at 45 ° intervals in an annular spring housing groove 30a formed on the outer peripheral surface of the cylinder 30 with a small diameter. An outer spring guide 60 closed on the right end side is fitted to the outer periphery of the cylinder 30 so as to be slidable in the axial direction, and an actuator is provided at the right closing portion of the outer spring guide 60 and the right step of the spring housing groove 30a. The right end side of the spring 34 is locked, and the inner spring guide 61 that supports the left end side of the actuator spring 34 is locked to the left step of the spring housing groove 30a. Both ends of the outer spring guide 60 in the axial direction are locked between the inner races of the pair of ball bearings 32 and 33 so as not to move in the axial direction, and the outer race is engaged with the inner peripheral surface of the slide cam 31 so as not to move in the axial direction. Stopped.

  Therefore, the outer spring guide 60, the pair of ball bearings 32 and 33, and the slide cam 31 are integrated, and when the slide cam 31 can move freely in the axial direction, when the cylinder 30 moves in the axial direction, the actuator spring 34. Without being compressed, the slide cam 31 moves integrally with the cylinder 30 in the axial direction. On the other hand, in a state where the movement of the slide cam 31 in the axial direction is restricted, when the cylinder 30 moves in the axial direction, the actuator springs 34 are compressed so that only the cylinder 30 remains in the axial direction while the slide cam 31 is stopped. Can be moved to. Therefore, the slide cam 31 is floatingly supported in the axial direction by the cylinder 30 via the actuator springs 34.

  As shown in FIG. 2 to FIG. 5 and FIG. 13, six arc-shaped cam grooves 31 a are recessed in the axial direction at intervals of 60 ° on the outer peripheral surface of the substantially cylindrical slide cam 31. The cam grooves 31a are provided with annular first and second convex portions 31b, 31c, and so on projecting radially outward at two locations in the middle. The positions of the six first protrusions 31b of the six cam grooves 31a are aligned in the axial direction, and the positions of the other six second protrusions 31c are also aligned in the axial direction. The top positions of the first and second convex portions 31b, 31c, ... are lower in the radial direction than the height of the outer peripheral surface of the slide cam 31.

  Six guide grooves 31d... Extending in the axial direction are formed on the outer peripheral surface of the slide cam 31 at intervals of 60 °, and rod-like sliders 64 are slidably fitted into the respective guide grooves 31d. A cam groove 64a extending in the axial direction is formed on the outer peripheral surface of each slider 64, and first and second recesses 64b and 64c that are recessed radially inward are formed at two midpoints of the cam groove 64a. . The positions of the six first recesses 64b of the six cam grooves 31a are aligned in the axial direction, and the positions of the other six second recesses 64c are also aligned in the axial direction.

  Six spring storage grooves 31e are formed on the outer peripheral surface of the slide cam 31 adjacent to the six guide grooves 31d, and a slider spring 65 stored in each spring storage groove 31e is a slider 64. It is latched by the spring seat 64d protruding from the side surface of the. By the slider spring 65, the slider 64 is urged to the left in the axial direction with respect to the slide cam 31, and is held at a position in contact with a stopper surface 31f formed on the left side of the spring housing groove 31e.

  Therefore, in a state where the slider 64 can freely move to the left in the axial direction, when the slide cam 31 moves to the left, the slider pull 65 is not compressed, and the slider 64 moves to the left integrally with the slide cam 31. On the other hand, when the slide cam 31 moves to the left while the movement of the slider 64 to the left is restricted, the slider spring 65 is compressed, so that only the slide cam 31 moves to the left while the slider 64 is stopped. be able to. Therefore, the slider 64 is floatingly supported in the axial direction by the slide cam 31 via the slider spring 65.

  As apparent from FIGS. 7 to 12 and FIG. 14, the outer peripheral surface of the output shaft 12 is formed in a groove shape over the entire length in the axial direction, and is recessed to the intermediate portion in the thickness direction of the output shaft 12. Six strut housing grooves 66 are formed. Each strut accommodation groove 66 penetrates the output shaft 12 so as to communicate with the edges on both sides in the circumferential direction of the strut accommodation groove 66 at positions facing the inner peripheral surface of the first to seventh speed driven gears 21 to 27. A headball storage hole 67 and a tailball storage hole 68 are formed. The cam groove 31 a of the slide cam 31 faces the inner side in the radial direction of the headball storage hole 67, and the cam groove 64 a of the slider 64 faces the inner side of the end ball storage hole 68 in the radial direction. A large-diameter headball 69 is fitted in the headball storage hole 67 and the cam groove 31a of the slide cam 31 so as to be movable in the radial direction, and a small-diameter tailball is inserted in the tailball storage hole 67 and the cam groove 65a of the slider 65. 70 is fitted so as to be movable in the radial direction.

  The strut 71 housed in the strut housing groove 66 includes a main body portion 71a having an upper surface (radially outer surface) formed in an arcuate shape, and a first engagement surface extending in a generally radial direction on the rotation direction delay side of the main body portion 71a 71b, a second engagement surface 71c extending substantially in the radial direction on the rotational direction advance side of the main body portion 71a, and a third engagement surface extending in the generally circumferential direction continuously to the radially outer end of the first engagement surface 71b. 71d, an arm portion 71e extending from the first engagement surface 71b to the rotation direction advance side, and a pair of set ring engagement portions 71f and 71f formed on both sides of the main body portion 71a.

  Six notches 72 are formed on the inner peripheral surface of each of the first to seventh speed driven gears 21 to 27 corresponding to the six struts 71. Are formed with a drive surface 72a that can be engaged with the first engagement surface 71b of the strut 71 and an inclined surface 72b that guides the third engagement surface 71d of the strut 71. The head ball 69 faces the lower surface (radial inner side surface) of the first engagement surface 71b of the strut 71 so that the head ball 69 can come into contact therewith, and the tail ball 70 is formed on the lower surface (radial inner side surface) of the arm portion 71e of the strut 71. Opposite to contact.

  8 to 12, the head ball 69 in the head ball storage hole 67 of the output shaft 12 is pushed up radially outward by the first convex portion 31 b of the cam groove 31 a of the slide cam 31. The strut 71 pushed up at the lower portion of the first engaging surface 71b is caused to abut on the lower surface of the first speed driven gear 21 with the fulcrum a of the main body portion 71a in a counterclockwise direction in the figure, and the arm portion 71e serves as an output shaft. 12 shows a state in which the tail ball 70 inside the 12 tail ball storage holes 68 is dropped into the bottom of the first recess 64 b of the slider 64.

  In this state, the drive surface 72a of the notch 72 of the first speed driven gear 21 driven in the direction of arrow A by the first speed drive gear 14 is engaged with the first engagement surface 71b of the strut 71, and the second of the strut 71 is second. When the engaging surface 71 c abuts on the driven surface 66 a of the strut housing groove 66 of the output shaft 12, the driving force of the first speed driven gear 21 is transmitted to the output shaft 12 through the six struts 71.

  The notch 72 of the strut storage groove 66 of the output shaft 12, the headball storage hole 67, the tailball storage hole 68, the headball 69, the tailball 70, the strut 71, and the first to seventh speed driven gears 21 to 27 is the clutch of the present invention. The mechanism 35 is configured.

  The 1st to 7th driven gears 21 to 27 are assembled to the output shaft 12 as follows. The first-speed driven gear 21 will be described as an example. First, the headballs 69 and the tailballs 70 are respectively stored in the headball storage holes 67 and the tailball storage holes 68 on the outer periphery of the output shaft 12, and the radially outer sides thereof are stored. The struts 71 are housed in the strut housing groove 66 so as to be pressed. A pair of set rings 73 cut along one circumferential direction as a key groove are arranged on both sides in the axial direction of the struts 71 on the outer periphery of the output shaft 12, and the set ring engaging portions 71 f of the struts 71. By pressing from the outside in the direction, the head balls 69, tail balls 70, and struts 71 are held so as not to fall off. Then, the bush 28 is fitted to the outer periphery of the set ring 73, and the set ring 73 and the bush 28 are locked to the output shaft 12 by the key 74 so as not to be relatively rotatable.

  As described above, the strut 71, the head ball 69, and the tail ball 70 are temporarily fixed by the set ring 73 so as not to drop from the output shaft 12, and the strut 71 can be positioned in the axial direction by the set ring 73. Improves.

  Each of the 1st to 7th driven gears 21 to 27 is rotatably supported by two bushes 28 and 28, and between the two bushes 28 and 28, a strut 71..., A headball 69. Is supported. In this way, the first to seventh speed driven gears 21 to 27 are assembled in order from the right side to the left side of the output shaft 12 according to the arrangement order, and the rightmost first speed driven gear 21 is attached to the stopper projection 12a of the output shaft 12. The first-speed to seventh-speed driven gears 21 to 27 are locked by a spacer 75 and the leftmost six-speed driven gear 27 is locked by a sensor ring 77 fixed to the output shaft 12 by a circlip 76. Is supported on the output shaft 12.

  The bushes 28, which support the 1st to 7th driven gears 21 to 27 so as to be rotatable relative to the output shaft 13, support both end portions in the axial direction while avoiding the central portion in the axial direction of each gear. A space for arranging the clutch mechanism 35 can be secured. In addition, since the two opposite end portions of two adjacent gears are supported by one bush 28, the number of bushes 28 can be minimized.

The engagement relationship between the output shaft 12 and the 1st to 7th driven gears 21 to 27 is as follows:
(1) Engagement state (see Fig. 15)
(2) One-way condition (see Fig. 16)
(3) Non-engaged state (see Fig. 17)
The three states can be switched.

  First, the engaged state (1) will be described. In FIG. 15, the head ball 69 and the first engagement surface 71 b of the strut 71 are pushed up radially outward by the first convex portion 31 b of the cam groove 31 a of the slide cam 31, and the tail ball 70 is pushed by the arm portion 71 e of the strut 71. Is shown in a state of being pushed into the first recess 64b of the slider 64 (that is, the state described with reference to FIGS. 8 to 12).

  During acceleration in this engaged state (see FIG. 15A), as already described, when the first speed driven gear 21 rotates in the direction of arrow A, the rotation is transmitted to the output shaft 12 via the strut 71. Thus, the rotation of the input shaft 11 is transmitted to the output shaft 12 while being decelerated via the first speed drive gear 14 and the first speed driven gear 21.

  On the other hand, at the time of deceleration (see FIG. 15B), the first speed driven gear 21 rotates in the opposite direction (arrow B) relative to the output shaft 12, but the first speed driven gear 21 is driven. The force is transmitted from the inclined surface 72b to the output shaft 12 through the first engagement surface 71b of the strut 71, the head ball 69, and the head ball storage hole 67, whereby the transmission state of the driving force is maintained. Therefore, at the time of deceleration, the driving force can be transmitted back from the driving wheel side to the engine side, and the engine brake can be operated without any trouble.

  Next, the one-way state (2) will be described. As shown in FIG. 16, in the one-way state, the lower surface of the head ball 69 faces the cam groove 31 a of the slide cam 31, and the lower surface of the tail ball 70 faces the first recess 64 b of the slider 64.

  In this state, when the first-speed driven gear 21 is accelerated in the direction of arrow A (see FIG. 16A), the head ball 69 may not be pushed up by the first convex portion 31b of the cam groove 31a of the slide cam 31. As the head ball 69 is pushed up radially outward by centrifugal force, transmission of the driving force is maintained in the same manner as during acceleration of the engaged state (see FIG. 15A).

  In this way, the head ball 69 is moved radially outward by centrifugal force during the transition from the time of acceleration in the engaged state (see FIG. 15A) to the time of acceleration in the one-way state (see FIG. 16A). By energizing, the transmission of the driving force is continued without interruption, so that the one-way state can be established without being affected by the operation speed of the shifting operation for moving the slide cam 31.

  On the other hand, at the time of deceleration (see FIG. 16B), the first speed driven gear 21 rotates in the opposite direction (arrow B) relative to the output shaft 12, so that the notch 72 of the first speed driven gear 21 The strut 71 having the third engagement surface 71d pressed against the inclined surface 72b swings clockwise from the solid line position to the chain line position, so that the first engagement surface 71b of the strut 71 and the notch 72 of the first speed driven gear 21 are provided. And the first speed driven gear 21 slips with respect to the output shaft 12.

  Next, the non-engagement state (3) will be described. As shown in FIG. 17, in the disengaged state, the lower surface of the head ball 69 faces the cam groove 31 a of the slide cam 31, and the lower surface of the tail ball 70 faces the cam groove 64 a of the slider 64.

  In this state, the tail ball 70 pushed up into the cam groove 31a of the slider 64 pushes up the arm portion 71e of the strut 71, and the head ball 69 falls into the cam groove 31a of the slide cam 31, so that the strut 71 rotates around the fulcrum a. And the first engagement surface 71b of the strut 71 and the drive surface 72a of the notch 72 of the first speed driven gear 21 are disengaged, and the first speed driven gear 21 outputs regardless of whether it is accelerated or decelerated. Slip with respect to the shaft 12.

  The engagement state, the one-way state, and the non-engagement state of the first speed driven gear 21 have been described above, but the operation of the second speed driven gear to the seventh speed driven gears 22 to 27 is the same. However, the head balls 69 of the first gear, the third gear, the fifth gear, and the seventh gear driven gears 21 to 24 are pushed up by the first convex portion 31b of the cam groove 31a of the slide cam 31, and the tail ball 70 is moved to the first concave portion 64b of the slider 64. However, the head ball 69 of the second gear, the fourth gear, and the sixth gear driven gear 25 to 27 is pushed up by the second convex portion 31 c of the cam groove 31 a of the slide cam 31, and the tail ball 70 is moved to the second concave portion of the slider 64. It differs in that it falls to 64c.

  Table 1 shows that the stroke of the actuator (cylinder 30) between the neutral gear position normal position and the seventh speed gear position is divided into 21 stages “0” to “20”, and the first to seventh speed driven gears 21 to 21 of each stage. 27 states are shown. “◯” in the table indicates the engaged state, “X” indicates the disengaged state, and “−” indicates the one-way state. US @ Acc indicates upshift in acceleration state, US @ Dec indicates upshift in deceleration state, DS @ Acc indicates downshift in acceleration state, DS @ Dec indicates downshift in deceleration state Is shown.

  Seven areas shaded in the table indicate actuator strokes at which transmission of driving force is interrupted. The 1st to 7th indications corresponding to the seven regions sandwiched between the shaded portions represent the driven gears 21 to 27 that transmit the driving force in the actuator stroke. What is characteristic here is that during US @ Acc (shifting up in an acceleration state), the driving force is transmitted in all strokes “1” to “20” except the actuator stroke “0” (neutral gear). Upshifting is performed without interruption.

  Hereinafter, based on FIGS. 18 to 34, the neutral gear shifts up to the third gear through the first gear and the second gear, and then passes again through the second gear and the first gear to the neutral. The operation when shifting down to the gear position will be described in detail.

  FIG. 18 corresponds to the actuator stroke “0” in Table 1. The cylinder 30 is at the limit position on the right side, and the first convex portion 31 b of the cam groove 31 a of the slide cam 31 is adjacent to the right side of the first speed driven gear 21. The second convex portion 31 c of the cam groove 31 a of the slide cam 31 is positioned so as to be separated from the right side of the second speed driven gear 25. The first recess 64b of the slider 64 provided on the slide cam 31 is positioned adjacent to the right side of the first speed driven gear 21 and the second recess 64c of the slider 64 is positioned apart from the right side of the second speed driven gear 25. .

  Accordingly, the tail ball 70 in the first speed gear stage is pushed up by the slider 64, and the head ball 69 falls into the cam groove 31a of the slide cam 31, so that the strut 71 swings in the clockwise direction, and the first speed driven gear 21 and the output. The engagement of the shaft 12 is in a released state (non-engaged state), and the 2nd to 7th driven gears 22 to 27 are similarly disengaged, and transmission of driving force via the transmission T is performed. I will not.

  FIG. 19 corresponds to the actuator stroke “2” in Table 1. The cylinder 30 moves to the left and the first convex portion 31b of the cam groove 31a of the slide cam 31 pushes up the head ball 69 of the first speed gear stage, and When the tail ball 70 falls into the first recess 64 b of the slider 64, the strut 71 swings counterclockwise to be engaged, and the rotation of the first speed driven gear 21 is transmitted to the output shaft 12 via the strut 71. A first gear is established. At this time, the 2nd to 7th driven gears 22 to 27 are still in the disengaged state.

  FIG. 20 corresponds to the actuator stroke “3” in Table 1. The cylinder 30 moves to the left and the first convex portion 31b of the cam groove 31a of the slide cam 31 passes over the head ball 69 of the first speed gear stage. A cam groove 31 a of the slide cam 31 faces the lower side of the head ball 69. However, the head ball 69 remains pushed up radially outward by centrifugal force, and the rotation of the first speed driven gear 21 is still transmitted to the output shaft 12 via the strut 71. That is, the first gear is in the one-way state, and transmission of driving force continues without interruption. At this time, the 2nd to 7th driven gears 22 to 27 are still in the disengaged state.

  FIG. 21 also corresponds to the actuator stroke “3” in Table 1. The cylinder 30 is further moved to the left as compared with the state of FIG. 20, but the slide spring 31 is compressed by the compression of the actuator springs 34. It remains in the position of FIG. Even in this state, the first gear is in the one-way state, and transmission of the driving force continues without interruption. The reason why the actuator springs 34 are compressed and the slide cam 31 stays in the position shown in FIG. 20 is that the second-speed gear stage tail ball 70 rides on the cam groove 64a of the slider 64 and the strut 71 cannot swing counterclockwise. Therefore, the head ball 69 is blocked by the strut 71 and cannot move radially outward, and the left movement of the slide cam 31 with the second convex portion 31c locked to the head ball 69 is blocked. is there.

  FIG. 22 also corresponds to the actuator stroke “3” in Table 1. The first gear is in the one-way state, and transmission of driving force continues without interruption. When the second speed driven gear 25 rotates relative to the output shaft 12 and the notch 72 reaches the outer side in the radial direction of the strut 71, the head is pushed up while pushing the first engagement surface 71 b of the strut 71 into the notch 72. The ball 69 can move radially outward, and at the same time, the slide cam 31 can also move to the left by the elastic force of the compressed actuator springs 34. However, in this state, since the first engaging surface 71b of the strut 71 of the second speed gear stage has not yet engaged with the drive surface 72a of the notch 72 of the second speed driven gear 25, the second speed gear stage has not been established. is there.

  Thus, even if the cylinder 30 moves to the left, the slide cam 31 is stopped while compressing the actuator springs 34, and the second speed driven gear 25 is rotated so that the strut 71 can be engaged with the notch 72. Then, the slide cam 31 is moved to the left by the elastic force of the actuator springs 34 to push up the head ball 69 by the second convex portion 31c and swing the strut 71 into the notch 72. Regardless of the moving speed, the strut 71 can be automatically swung at an appropriate timing.

  At this time, the strut 71 at the first speed shift stage engages with the drive surface 72a of the notch 72 of the first speed driven gear 21 to transmit the driving force, so the strut 71 cannot swing clockwise. The tail ball 70 is restrained by the strut 71 and cannot move radially outward. As a result, even if the slide cam 31 moves to the left, the slider 64 whose cam groove 64a is restrained by the tail ball 70 cannot move to the left together with the slide cam 31, and the slider 64 compresses the slider spring 65. It is left behind from the slide cam 31.

  FIG. 23 corresponds to the actuator strokes “4” and “5” in Table 1. The drive surface 72a of the notch 72 of the second speed driven gear 25 is engaged with the first engagement surface 71b of the strut 71 and 2 A speed gear is established, and the rotational speed of the output shaft 12 is increased by the second speed. As a result, the first speed driven gear 21 rotates in the reverse direction relative to the output shaft 12, and the engagement between the first engagement surface 71b of the strut 71 and the drive surface 72a of the notch 72 of the first speed driven gear 21 is released. Is done. As a result, the strut 71 can freely swing, and the slider 64 that has been restrained while compressing the slider spring 65 is moved to the left by the elastic force of the slider spring 65. As a result, the tail ball 70 of the first speed shift stage rides on the cam groove 64a of the slider 64 and is pushed up, and the strut 71 swings clockwise to drop the head ball 69 into the cam groove 31a of the slide cam 31. The speed driven gear 21 can be rotated relative to the output shaft 12 and the first gear is released.

  During the transition from the state of FIG. 22 to the state of FIG. 23, the cylinder 30 stays at the position a and the slide cam 31 stays at the position b, but does not move, but the slider 64 is c by the elastic force of the compressed slider spring 65. Left-shift from position to c 'position to release first gear. In this way, by moving the slider 64 and moving the shift operation without moving the cylinder 30, the total required stroke amount of the cylinder 30 can be reduced and the axial dimension of the transmission T can be reduced. it can.

  FIG. 24 corresponds to the actuator stroke “6” in Table 1. The cylinder 30 moves to the left and the second convex portion 31c of the cam groove 31a of the slide cam 31 passes over the headball 69 of the second speed gear stage. A cam groove 31 a of the slide cam 31 faces the lower side of the head ball 69. However, the head ball 69 remains pushed up radially outward by centrifugal force, and the rotation of the second speed driven gear 25 is still transmitted to the output shaft 12 via the strut 71. That is, the second gear is in the one-way state, and driving force transmission continues without interruption. At this time, the gears other than the second speed driven gear 25 are in an unengaged state.

  FIG. 25 also corresponds to the actuator stroke “6” in Table 1. The cylinder 30 is further moved to the left as compared with the state of FIG. 25, but the slide spring 31 is compressed by the compression of the actuator springs 34. It remains in the position of FIG. Even in this state, the second gear is in the one-way state, and transmission of the driving force continues without interruption. The reason why the actuator springs 34 are compressed and the slide cam 31 stays at the position shown in FIG. 25 is that the tail ball 70 of the third speed gear stage rides on the cam groove 64a of the slider 64 and the strut 71 cannot swing counterclockwise. Therefore, the head ball 69 is blocked by the strut 71 and cannot move radially outward, and the left movement of the slide cam 31 with the first convex portion 31b locked to the head ball 69 is blocked. is there.

  FIG. 26 also corresponds to the actuator stroke “6” in Table 1. The second gear is in the one-way state, and transmission of the driving force continues without interruption. When the third speed driven gear 22 rotates relative to the output shaft 12 and the notch 72 reaches the outer side in the radial direction of the strut 71, the head is pushed up while pushing the first engagement surface 71 b of the strut 71 into the notch 72. The ball 69 can move radially outward, and at the same time, the slide cam 31 can also move to the left by the elastic force of the compressed actuator springs 34. However, in this state, since the first engagement surface 71b of the strut 71 of the third speed gear stage has not yet engaged with the drive surface 72a of the notch 72 of the third speed driven gear 22, the third speed gear stage has not been established. is there.

  Thus, even if the cylinder 30 moves to the left, the slide cam 31 is stopped while compressing the actuator springs 34, and the third speed driven gear 22 is rotated so that the strut 71 can be engaged with the notch 72. Then, the slide cam 31 is moved to the left by the elastic force of the actuator springs 34 to push up the head ball 69 by the first convex portion 31b and swing the strut 71 into the notch 72. Regardless of the moving speed, the strut 71 can be automatically swung at an appropriate timing.

  At this time, since the strut 71 at the second speed gear stage is engaged with the drive surface 72a of the notch 72 of the second speed driven gear 25 to transmit the driving force, the strut 71 cannot swing clockwise. The tail ball 70 is restrained by the strut 71 and cannot move radially outward. As a result, even if the slide cam 31 moves to the left, the slider 64 whose cam groove 64a is restrained by the tail ball 70 cannot move to the left together with the slide cam 31, and the slider 64 compresses the slider spring 65. It is left behind from the slide cam 31.

  FIG. 27 corresponds to the actuator strokes “7” and “8” in Table 1. The drive surface 72a of the notch 72 of the third speed driven gear 22 is engaged with the first engagement surface 71b of the strut 71 to achieve 3 A speed gear is established, and the rotational speed of the output shaft 12 is increased by the third speed. As a result, the second speed driven gear 25 rotates in the reverse direction relative to the output shaft 12, and the engagement between the first engagement surface 71b of the strut 71 and the drive surface 72a of the notch 72 of the third speed driven gear 22 is released. Is done. As a result, the strut 71 can freely swing, and the slider 64 that has been restrained while compressing the slider spring 65 is moved to the left by the elastic force of the slider spring 65. As a result, the tail ball 70 of the second speed shift stage rides on the cam groove 64a of the slider 64 and is pushed up, and the strut 71 swings clockwise to drop the head ball 69 into the cam groove 31a of the slide cam 31. The speed driven gear 25 can rotate relative to the output shaft 12 and the second speed gear stage is released.

  During the transition from the state of FIG. 26 to the state of FIG. 27, the cylinder 30 remains in the position a and the slide cam 31 remains in the position b and does not move, but the slider 64 is c by the elastic force of the compressed slider spring 65. Left-shift from the position to the c 'position to release the second gear. In this way, by moving the slider 64 and moving the shift operation without moving the cylinder 30, the total required stroke amount of the cylinder 30 can be reduced and the axial dimension of the transmission T can be reduced. it can.

  The process of upshifting from the neutral gear stage to the third gear stage has been described above, but the process of upshifting from the third gear stage to the seventh gear stage is substantially the same as described above. A duplicate description is omitted. Hereinafter, the process of downshifting from the third gear to the neutral gear will be described.

  FIG. 28 corresponds to the actuator strokes “7” and “6” in Table 1. When the slide cam 31 moves to the right together with the piston 30 moving to the right, the first convex portion of the cam groove 31a of the slide cam 31 is shown. 31b moves from the lower side to the right side of the head ball 69 of the third speed gear stage, the head ball 69 falls into the cam groove 31a, and the cam groove 64a of the slider 64 pushes up the tail ball 70, so that the strut 71 The first engaging surface 71b is disengaged from the drive surface 72a of the notch 72 of the third speed driven gear 22 by swinging in the direction, and the third speed gear stage is released. At this time, the tail ball 70 of the second speed gear stage faces the second recess 64c of the slider 64, and the head ball 69 is urged radially outward by centrifugal force, but the notch 72 of the second speed driven gear 25 is strutted. Since the position 71 has not been reached, the second gear is not yet established.

  FIG. 29 corresponds to the actuator stroke “6” in Table 1. Even if the piston 30 further moves to the right, the notch 72 of the second speed driven gear 25 does not reach the position of the strut 71, so that it is blocked by the strut 71. Thus, the head ball 69 cannot move radially outward, and the first convex portion 31b is caught by the head ball 69, so that the slide cam 31 cannot move to the right. As a result, the cylinder 30 moves to the right while compressing the actuator spring 34 while leaving the slide cam 31 in the position shown in FIG. In the state of this actuator stroke “6”, transmission of the driving force is temporarily interrupted.

  FIG. 30 corresponds to the actuator stroke “5” in Table 1. When the notch 72 of the second speed driven gear 25 reaches the position of the strut 71, the first engagement surface 71b of the strut 71 is engaged with the notch 72. As a result, the head ball 69 can move radially outward. As a result, the slide cam 31 moves right so as to follow the cylinder 30 by the elastic force of the compressed actuator spring 34, and the second convex portion 31 c of the cam groove 31 a of the slide cam 31 pushes up the head ball 69. A second gear is established. The method of transmitting the driving force at this time is the same as that during deceleration described with reference to FIG.

  Thus, even if the cylinder 30 moves to the right, the slide cam 31 is stopped while compressing the actuator springs 34, and the second speed driven gear 25 is rotated so that the strut 71 can be engaged with the notch 72. Then, the slide cam 31 moves to the right by the elastic force of the actuator springs 34 to push up the head ball 69 by the second convex portion 31c and swing the strut 71 into the notch 72. Regardless of the moving speed, the strut 71 can be automatically swung at an appropriate timing.

  FIG. 31 corresponds to the actuator strokes “4” and “3” in Table 1. When the slide cam 31 moves to the right together with the piston 30 moving to the right, the second convex portion of the cam groove 31a of the slide cam 31 is shown. 31c moves from the lower side to the right side of the head ball 69 of the second gear, the head ball 69 falls into the cam groove 31a, and the cam groove 64a of the slider 64 pushes up the tail ball 70, so that the strut 71 The first engagement surface 71b is disengaged from the drive surface 72a of the notch 72 of the second speed driven gear 25, and the second speed gear stage is released. At this time, the tail ball 70 of the first gear stage faces the cam groove 64a of the slider 64, and the head ball 69 is urged radially outward by centrifugal force, but the notch 72 of the first speed driven gear 21 is strut 71. Since the position has not been reached, the first gear is in an unestablished state.

  FIG. 32 corresponds to the actuator stroke “3” in Table 1. Even when the piston 30 further moves to the right, the notch 72 of the first speed driven gear 21 does not reach the position of the strut 71, so that it is blocked by the strut 71. Thus, the head ball 69 cannot move radially outward, and the slide cam 31 cannot move right because the first convex portion 31 b is caught by the head ball 69. As a result, the cylinder 30 moves to the right while compressing the actuator spring 34 while leaving the slide cam 31 in the position shown in FIG. In the state of this actuator stroke “3”, the transmission of the driving force is temporarily interrupted.

  FIG. 33 corresponds to the actuator stroke “2” in Table 1. When the notch 72 of the first speed driven gear 21 reaches the position of the strut 71, the first engagement surface 71 b of the strut 71 is engaged with the notch 72. As a result, the head ball 69 can move radially outward. As a result, the slide cam 31 moves right so as to follow the cylinder 30 by the elastic force of the compressed actuator spring 34, and the first convex portion 31 b of the cam groove 31 a of the slide cam 31 pushes up the head ball 69. The first gear is established. The method of transmitting the driving force at this time is the same as that during deceleration described with reference to FIG.

  Thus, even if the cylinder 30 moves to the right, the slide cam 31 is stopped while compressing the actuator springs 34, and the first speed driven gear 21 is rotated so that the strut 71 can be engaged with the notch 72. Then, the slide cam 31 moves to the right by the elastic force of the actuator springs 34 to push up the head ball 69 by the first convex portion 31b and swing the strut 71 into the notch 72. Regardless of the moving speed, the strut 71 can be automatically swung at an appropriate timing.

  FIG. 34 corresponds to the actuator stroke “0” in Table 1. The cylinder 30 further moves to the right so that the first convex portion 21b of the slide cam 31 is disengaged from the head ball 69 of the first speed gear stage, and the slider 64 When the cam groove 64a pushes up the tail ball 70, the strut 71 is disengaged and the first gear is released. At this time, the second gear to the seventh gear are similarly disengaged to establish a neutral gear.

  As described above, the output shaft 12 that supports the first to seventh speed driven gears 21 to 27 so as to be relatively rotatable can accommodate the strut storage groove 66 and the headball storage corresponding to each of the first to seventh speed driven gears 21 to 27. A hole 67 and a tail ball storage hole 68 are formed, and a head ball 69 stored in the head ball storage hole 67 and a tail ball stored in the tail ball storage hole 68 are formed at both circumferential ends of the strut 71 stored in the strut storage groove 66. 70, the head ball 69 and the tail ball 70 are pressed in the radial direction by the slide cam 31 that slides in the axial direction to swing the strut 71, so that the strut 71 and the first to seventh speed driven gears The engagement relationship with the notch 72 formed in each of 21 to 27 can be arbitrarily changed.

  As a result, the driving force can be transmitted from the driven gear side to the output shaft 12 side during acceleration, and the driving force can be transmitted from the driven gear side to the output shaft 12 side during acceleration. A one-way state in which the driving force cannot be transmitted from the driven gear side to the output shaft 12 side during deceleration, and a non-engaged state in which the driving force cannot be transmitted from the driven gear side to the output shaft 12 side during either acceleration or deceleration. It becomes possible to switch.

  In the non-engaged state, the strut 71 is forcibly retracted into the strut housing groove 66 of the output shaft 12, so that friction acts between the strut 71 and the 1st to 7th driven gears 21 to 27. Therefore, a decrease in drive efficiency due to friction can be minimized.

  Further, during acceleration in the engaged state shown in FIG. 15A and during acceleration in the engaged state shown in FIG. 16A, that is, when the driving force to be transmitted is large, the driving force is the first engagement of the strut 71. A surface contact portion between the mating surface 71b and the driving surface 72a of the concave portion 72 of the first to seventh speed driven gears 21 to 27, a second engaging surface 71c of the strut 71, and a non-driving portion 66a of the strut accommodation groove 66 of the output shaft 12. And is not transmitted via the head ball 69, so that local wear and deformation of the strut 71 due to spherical point contact can be prevented and durability can be improved. In addition, the headball 69 does not need to transmit a large load, and thus can be miniaturized. As a result, it can contribute to miniaturization of the axial dimension of the transmission T.

  In addition, at the time of deceleration in the engaged state shown in FIG. 15B, the driving force is transmitted to the headball storage hole 67 of the output shaft 12 through the headball 69, and in this case, a spherical point contact is obtained. In general, since the driving force transmitted during deceleration is small, there is no practical problem.

  When shifting up during acceleration, the low-speed gear stage is maintained in the one-way state from when the low-speed gear stage is disengaged until the high-speed gear stage is engaged. . As shown in FIG. 16A, since driving force is transmitted in the one-way state during acceleration, the high-speed gear shift stage is engaged after the low-speed gear shift stage is disengaged. Until then, transmission of the driving force is continued without interruption, and the acceleration performance of the vehicle can be maximized.

  Further, the first, third, fifth, and seventh speed driven gears 21 to 24, which are the odd-numbered shift stages, are collectively arranged at a predetermined interval from the right side to the left side of the output shaft 12, and are the even-numbered shift stages. The second gear, the fourth gear, and the sixth gear driven gears 25 to 27 are collectively arranged at a predetermined interval from the right side to the left side of the output shaft 12, and the first convex portions 31b ... of the slide cam 31 and the first concave portions 64b of the slider 64 ... The first, third, fifth, and seventh speed driven gears 21 to 24 are operated with the struts 71 and the second convex portions 31c of the slide cam 31 and the second concave portions 64c of the slider 64 with second and fourth speeds. Because the struts 71 of the 6-speed driven gears 25 to 27 are operated, the required stroke of the slide cam 31 from the first-speed shift position establishment position to the seventh-speed shift position establishment position, or the first-speed shift from the seventh speed shift position establishment position. It is possible to reduce the required stroke of the slide cam 31 to establish position.

  That is, the required stroke of the slide cam 31 can be reduced as the distance between two adjacent first-speed to seventh-speed driven gears 21 to 27 arranged on the output shaft 12 is reduced. The distance cannot be reduced without restriction by the axial dimension of 71 or the like.

  However, according to the present embodiment, when the first convex portions 31b and the first concave portions 64b are in an intermediate position between the first speed driven gear 21 and the second speed driven gear 25, the second convex portions 31c and the second concave portions are provided. 64c establishes the second speed shift stage, and when the second convex portion 31c and the second concave portion 64c are in an intermediate position between the second speed driven gear 25 and the fourth speed driven gear 26, the first convex portion 31b. When the recesses 64b... Establish the third speed shift stage, and the first protrusions 31b... And the first recesses 64b... Are in the middle position between the third speed driven gear 22 and the fifth speed driven gear 23, the second protrusions 31c. When the second recesses 64c... Establish the fourth speed shift stage, and the second protrusions 31c and the second recesses 64c... Are in the intermediate positions of the fourth speed driven gear 26 and the sixth speed driven gear 27, the first When the first and second recesses 31b,... And the first recesses 64c establish the fifth gear, and the first protrusions 31b and the first recesses 64b are at an intermediate position between the fifth speed driven gear 23 and the seventh speed driven gear 24. When the convex portions 31c and the second concave portions 64c establish the sixth speed, and when the second convex portions 31c and the second concave portions 64c pass the sixth speed driven gear 27 to the left side, the first convex portions 31b. And the first concave portion 64c establishes the seventh speed shift stage, so that the slide cam 31 is compared with the case where the single convex portion... And the single concave portion. The required stroke can be reduced to about half, which contributes to the reduction in the axial dimension of the transmission T.

  The speed change operation of the transmission T described above does not require the driving force to be interrupted by the speed change clutch, and can be performed while transmitting the driving force, so that the acceleration performance during acceleration can be ensured to the maximum.

  35 to 41 show a second embodiment of the present invention. FIG. 35 is a view corresponding to FIG. 2 (a cross-sectional view taken along the line 35-35 in FIG. 36), and FIG. 36 is a sectional view taken along line 37-37 of FIG. 35, FIG. 38 is a sectional view taken along line 38-38 of FIG. 35, FIG. 39 is an enlarged view of 39 part of FIG. 35, and FIG. FIG. 41 is an exploded perspective view of the periphery of the actuator spring. In the second embodiment, members corresponding to those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and redundant description is omitted.

  The first embodiment described above includes the slide cam 31 formed of a single member. However, as shown in FIG. 40, the slide cam 31 according to the second embodiment is divided into two shafts. The first slide cam 31R on the right side and the second slide cam 31L on the left side, which are floatingly supported so as to be relatively movable in the direction, are provided. In the first embodiment, six sliders 64... Made of different members are floatingly supported so as to be axially movable relative to each other. However, as shown in FIG. 40, the slide cam of the second embodiment is used. 31 is not provided with sliders 64, and cam grooves 64a, first recesses 64b, and second recesses 64c are formed directly on the surface of the slide cam 31.

  The first slide cam 31R and the second slide cam 31L mesh with each other in a comb-teeth shape so as to be able to move relative to each other in the axial direction, and the mesh line of the cam slide 31a guides the headball 69 in the width direction center and the tail. The cam groove 64a for guiding the ball 70 is set at the center in the width direction.

  As described above, since the first slide cam 31R and the second slide cam 31L are engaged with each other at the cam grooves 31a, 64a, etc. so as to be slidable in the axial direction, an increase in the axial dimension of the slide cam 31 is prevented. can do. In the meshing portion, the cam groove 31a for guiding the head ball 69 and the cam groove 64a for guiding the tail ball 70 are reduced to half of the other portions, but the head ball 69 and the tail ball 70 are output shafts. 12 is restrained by the head ball storage hole 67 and the tail ball storage hole 68, there is no possibility of falling off the narrow portions of the cam grooves 31a and 64a.

  Next, a structure in which the first and second slide cams 31R and 31L are independently floating supported with respect to the cylinder 30 will be described with reference to FIGS. 35, 36, 39, and 41. FIG.

  A pair of spring retainers 81, 81 divided into two on the diameter line are fitted into a spring housing groove 30a formed in a small diameter in the axial intermediate portion of the cylinder 30 so as to form a cylinder, and the outer periphery of the axial intermediate portion It is fixed with a retainer set clip 82 that fits into the. On the left and right outer peripheral surfaces of the pair of spring retainers 81, 81, eight arc grooves 81a having a semicircular cross section are formed at 45 ° intervals.

  The inner races of the two ball bearings 32 and 33 are slidably fitted to the outer side in the axial direction of the spring housing groove 30a of the cylinder 30. A pair of spring guide housings 83R and 83R divided into two on the diameter line are fitted between the inner race of the right ball bearing 32 and the central part of the spring retainers 81 and 81 so as to form a cylinder. Both ends are fixed by a ring 84 and a circlip 85, respectively, and the outer race of the ball bearing 82 is fixed to the first slide cam 31R by a pair of circlips 86 and 87. Similarly, a pair of spring guide housings 83L and 83L divided into two on the diameter line are fitted between the inner race of the left ball bearing 33 and the central part of the spring retainers 81 and 81 so as to form a cylinder. The left and right ends are fixed by a ring 84 and a circlip 85, respectively, and the outer race of the ball bearing 82 is fixed to the second slide cam 31L by a pair of circlips 86 and 87.

  As a result, the cylinder 30 and the spring retainers 81, 81 are integrated, the right spring guide housings 83R, 83R, the right ball bearing 82, and the right first slide cam 31R are integrated, and the left spring guide housing. 83L, 83L, the left ball bearing 83, and the left second slide cam 31L are integrated.

  Between the spring retainers 81, 81 and the right side spring guide housings 83R, 83R, a pair of spring guides 88, 89 fitted in a telescopic manner with the actuator spring 34 being retracted is housed. Similarly, between the spring retainers 81, 81 and the left spring guide housings 83L, 83L, the actuator spring 34 is housed in a contracted manner between a pair of spring guides 88, 89 that are fitted in an extendable manner.

  Therefore, when the cylinder 30 moves to the left, the load of the spring retainers 81, 81 → the right actuator spring 34... → the right spring guide housing 83R, 83R → the right ball bearing 82 → the circlip 86,87 It is transmitted to the first slide cam 31R, and at the same time, it is transmitted to the second slide cam 31L on the left side through the path of the spring retainers 81, 81 → the left actuator spring 34... → the left ball bearing 83 → the circlips 86,87. .

  When the cylinder 30 moves to the right, the load of the spring retainers 81, 81 → the left actuator spring 34... → the left spring guide housing 83L, 83L → the left ball bearing 83 → the circlip 86, 87 2 is transmitted to the slide cam 31L, and simultaneously, is transmitted to the first slide cam 31R on the right side through the path of the spring retainers 81, 81 → the right actuator spring 34... → the right ball bearing 82 → the circlips 86,87.

  If the first slide cam 31R on the right side is restrained so that it cannot move when the cylinder 30 moves in the left-right direction, only the cylinder 30 moves while compressing the right actuator spring 34 ... If the slide cam 31L is restrained so as not to move, only the cylinder 30 moves while compressing the left actuator springs 34.

  Therefore, in the state corresponding to FIG. 21 of the first embodiment, that is, in the process of shifting up from the first gear to the second gear, the second convex portion 31c of the second slide cam 31L on the left side is changed to the second gear. In a state where the left movement is prevented by the stepped head ball 69, the left second slide cam 31L temporarily stops the left movement, and only the cylinder 30 moves to the left while compressing the left actuator spring 34. As the second speed driven gear 25 rotates, the strut 71 swings into the notch 72 and the head ball 69 can move radially outward, and the left second slide cam 31L is released from the left side. It moves to the left so as to follow the cylinder 30 by the elastic force of the actuator springs 34.

  In the state corresponding to FIG. 25 of the first embodiment, that is, in the process of shifting up from the second gear to the third gear, the first convex portion 31b of the right first slide cam 31R is in the third gear. In the state where the left movement is prevented by the head ball 69, the first slide cam 31R on the right side temporarily stops the left movement, and only the cylinder 30 moves to the left while compressing the right actuator springs 34. When the strut 71 swings in the notch 72 and the head ball 69 can move radially outward with the rotation of the third speed driven gear 22, the first slide cam 31R on the right side is released from the right side. It moves to the left so as to follow the cylinder 30 by the elastic force of the actuator springs 34.

  In the state corresponding to FIG. 29 of the first embodiment, that is, in the process of shifting down from the third speed shift stage to the second speed shift stage, the second convex portion 31c of the left second slide cam 31L is moved to the second speed shift stage. In the state where the right movement is blocked by the head ball 69, the second slide cam 31L on the left side temporarily stops moving right, and only the cylinder 30 moves right while compressing the left actuator springs 34. As the second speed driven gear 25 rotates, the strut 71 swings into the notch 72 and the head ball 69 can move radially outward, and the left second slide cam 31L is released from the left side. It moves to the right so as to follow the cylinder 30 by the elastic force of the actuator springs 34.

  In the state of FIG. 32 of the first embodiment, that is, in the process of shifting down from the second gear to the first gear, the first convex portion 31b of the right first slide cam 31R is the head of the first gear. In a state where the right movement is prevented by the ball 69, the right first slide cam 31R temporarily stops moving right, and only the cylinder 30 moves right while compressing the right actuator spring 34. As the first-speed driven gear 21 rotates, the strut 71 swings into the notch 72 and the head ball 69 can move radially outward, and the right-side first slide cam 31R is released from the right-hand side. It moves to the right so as to follow the cylinder 30 by the elastic force of the actuator springs 34.

  As described above, according to the second embodiment, as in the case of the first embodiment described above, until the notch 72 of the driven gear of the rear shift stage reaches a position where it can engage with the strut 71. As the first and second slide cams 31R and 31L move with respect to the cylinder 30, the time lag until the subsequent shift stage is established is automatically absorbed, regardless of the moving speed of the cylinder 30. Smooth shift changes can be made possible. And according to 2nd Embodiment, since slider 64 ... and slider spring 65 ... can be abolished, the number of parts can be reduced and it can contribute to a cost reduction.

  Further, the first and second slide cams 31R and 31L and the actuator spring 34, which are divided into two parts in the second embodiment, function as the sliders 64 and the slider springs 65 in the first embodiment. Demonstrate. That is, in the state of FIG. 22 of the first embodiment, that is, in the process of shifting up from the first gear to the second gear, the strut 71 meshes with the notch 72 while the first gear is in the one-way state, and the driving force , The strut 71 cannot swing clockwise, and the tailball 70 is restrained by the strut 71 and cannot move radially outward.

  In such a case, in the second embodiment, even if the cylinder 30 tries to move to the left, the first slide cam 31R on the right side cannot move to the left because the first recess 64b is blocked by the tail ball 70, The first slide cam 31R is left behind from the cylinder 30 while compressing the right actuator springs 34. When the second gear is established and the first speed gear strut 71 is retracted into the strut housing groove 66, the right first slide cam 31R, which is released from the restraint by the tail ball 70, is compressed by the compressed actuator spring. It moves to the left so as to follow the cylinder 30 with the elastic force of 34.

  Further, in the state of FIG. 26 of the first embodiment, that is, in the process of shifting up from the second gear to the third gear, the strut 71 is engaged with the notch 72 and the driving force is increased while the second gear is in the one-way state. When transmitting, the strut 71 cannot swing clockwise, and the tailball 70 is restrained by the strut 71 and cannot move radially outward.

  In such a case, in the second embodiment, even if the cylinder 30 tries to move to the left, the second slide cam 31L on the left cannot move to the left because the second recess 64c is blocked by the tail ball 70, The second slide cam 31L is left behind from the cylinder 30 while compressing the left actuator springs 34. When the third speed gear stage is established and the second speed gear stage strut 71 retracts into the strut housing groove 66, the left second slide cam 31L, which is released from the restraint by the tail ball 70, is compressed by the compressed actuator spring. It moves to the left so as to follow the cylinder 30 with the elastic force of 34.

  As described above, when the first and second slide cams 31R and 32L are moved to the left by the compressed actuator spring 34, the cylinder 30 is stopped without moving to the left. The required stroke of the cylinder 30 can be reduced by the stroke of the two slide cams 31R and 31L, and the axial dimension of the transmission can be shortened.

  That is, in the second embodiment, when the next shift stage is established by the first slide cam 31R, the second slide cam 31L exhibits the function of the slider 64 of the first embodiment, and the next stage Is established by the second slide cam 31L, the first slide cam 31R exhibits the function of the slider 64 of the first embodiment.

  Other operations and effects of the second embodiment are the same as those of the first embodiment.

  42 to 61 show a third embodiment of the present invention. FIG. 42 is a view corresponding to FIG. 2 (a cross-sectional view taken along the line 42-42 in FIG. 43), and FIG. 44 is a cross-sectional view taken along the line 44-44 of FIG. 42, FIG. 45 is a perspective view of the slide cam, FIG. 46 is an enlarged view of 46 part of FIG. 45, and FIG. 48 is a cross-sectional view taken along line 48-48 of FIG. 47, FIG. 49 is an exploded perspective view of 49 portion of FIG. 48, FIG. 50 is a diagram showing a cam groove of a rotary barrel, and FIGS. It is operation | movement explanatory drawing at the time. In the third embodiment, members corresponding to those in the first and second embodiments are denoted by the same reference numerals as those in the first and second embodiments, and redundant description is omitted. .

  First, the structure of the transmission T will be described with reference to FIGS.

  In the first embodiment and the second embodiment, a single slide cam 31 (first embodiment) or a slide cam 31L, 31R divided into two by a cylinder 30 that moves in the axial direction by hydraulic pressure. Although the shift change is performed by moving the second embodiment in the axial direction, in the third embodiment, the slide cams 31A to 31A divided into four by the rotary barrel 91 that is rotated by an actuator such as an electric motor. A shift change is performed by moving 31D independently in the axial direction. That is, the slide cam 31 of the third embodiment is divided into four slide slides 31A to 31D.

  In the first and second embodiments, the first gear, the third gear, the fifth gear, and the seventh gear driven gears 21, 22, 23, and 24 are collectively arranged so that the second gear, the fourth gear, and the sixth gear driven gears 25, 26, 27 are arranged together, but in the third embodiment, two driven gears with non-continuous shift stages are arranged as a set. Specifically, the first-speed driven gear 21 and the third-speed driven gear 22 that form a set, the second-speed driven gear 25 and the fifth-speed driven gear 23 that form a set, the fourth-speed driven gear 26 that forms a set, A 6-speed driven gear 27 and a single 7-speed driven gear 24 are arranged. The arrangement of these gears is not limited to the embodiment, and the arrangement is arbitrary as long as the gear positions of the two driven gears forming the set are not continuous.

  The rotary barrel 91 arranged at the center of the hollow output shaft 12 can be reciprocally rotated in the range of 0 ° to 315 ° by an actuator 92 such as an electric motor arranged outside thereof, The four guide grooves 91a to 91d (see FIG. 50) spaced apart in the axial direction are formed in the circumferential direction. A cylindrical bearing holder 93 is coaxially disposed on the outer periphery of the rotary barrel 91, and the right end of the rotary barrel 91 is supported on the inner peripheral surface of the right end of the bearing holder 93 via a needle bearing 94 so as to be relatively rotatable. The left end of the rotary barrel 91 is supported on the inner peripheral surface of the left end of the bearing holder 93 via a ball bearing 95 so as to be relatively rotatable. A support tube 96 coupled to the left end of the bearing holder 93 is fixed to a casing (not shown) of the transmission T. Therefore, the bearing holder 93 is fixed so as not to rotate and to move in the axial direction with respect to the casing.

  Since the structure of the four slide cams 31A to 31D is substantially the same, the structure of the second slide cam 31B from the right will be described as a representative example. The structure of the slide cam 31B has a structure similar to that of the slide cams 31L and 31R of the second embodiment, and engages with the adjacent slide cam in a comb shape so as to be relatively movable in the axial direction. On the outer surface of the slide cam 31B, six cam grooves 31a for the head balls 69 and six cam grooves 64a for the tail balls 70 are alternately formed in the circumferential direction. Each cam groove 31a for the ball 69 is provided with one convex portion 31g, and each cam groove 64a for the tail ball 70 is provided with one concave portion 64e.

  The meshing portion of the slide cam 31B that meshes with two adjacent slide cams 31A and 31C in a comb-like shape is an intermediate position in the width direction of the six cam grooves 31a for the headballs 69, and 6 for the tailballs 70. The cam grooves 64a are formed at intermediate positions in the width direction. Further, six rectangular openings 31h (see FIG. 4) are formed between the cam grooves 31a for the head balls 69 of the slide cam 31B and the cam grooves 64a for the tail balls 70. .

  The slide cam 31B is supported on the outer peripheral surface of the bearing holder 93 via a ball bearing 97 so as to be relatively rotatable. The ball bearing 97 includes an inner race 97b and an outer race 97c sandwiching the balls 97a, the inner race 97b extends from the ball 07a to the left and the outer race 97c extends from the ball 97a to the right. The inner race 97b can slide in the axial direction along the outer peripheral surface of the bearing holder 93, and the outer race 97c can slide in the axial direction along the inner peripheral surface of the slide cam 31B.

  A pin 98 is press-fitted into a pin hole 97d formed in the inner race 97b. The pin 98 is guided along a slit 93a (see FIG. 48) formed in the axial direction in the bearing holder 93, and is radially inward. The end engages with the guide groove 91 b of the rotary barrel 91. The outer race 97c is formed with rectangular openings 97e that overlap the openings 31h of the slide cam 31B. A pair of spring guides 88 and 89 sandwiching the actuator spring 34 in a compressed state are attached to the opening 31h of the slide cam 31B and the opening 97e of the outer race 97c.

  Therefore, the slide cam 31B is supported in a floating manner with respect to the ball bearing 97, and when the ball bearing 97 moves in the axial direction with the movement of the slide cam 31B in the axial direction restricted, the actuator springs 34 are compressed. The relative movement between the two can be absorbed. This relationship is the same as the relationship between the left and right slide cams 31L and 31R in the second embodiment.

  The second slide cam 31B from the right operates the head ball 69 ... and the tail ball 70 ... of the second speed variable driven gear 25 located on the right side by moving to the right, and is located on the left side by moving left. The head balls 69 and tail balls 70 of the fast driven gear 23 can be operated. The action of the first and third slide cams 31A and 31C from the right is the same as the action of the second slide cam 31B described above, but the leftmost slide cam 31D performs only a right movement and moves to the right. The head ball 69... And the tail ball 70.

  The structure of the clutch mechanism 35 of the third embodiment is the same as that of the first and second embodiments described above. Although the first to seventh speed driven gears 21 to 27 are supported by the bushes 28 in the first and second embodiments, they are supported by the ball bearings 28 'in the third embodiment.

  Accordingly, when the rotary barrel 91 is rotated by the actuator 92, the pins 98... That engage with the four guide grooves 91a to 91d formed in the circumferential direction on the outer peripheral surface of the bearing holder 93 fixed to the casing. By being guided in the axial direction by the slits 93a, the ball bearings 97 pushed and pulled by the inner races 97b fitted to the outer peripheral surface of the bearing holder 93 move in the axial direction, and the outer surfaces of the ball bearings 97 are moved. The slide cams 31A to 31D connected to the races 97c through actuator springs 34 can independently move in the axial direction.

  At this time, since the bearing holder 93 is fixed to the casing, the inner race 97b of each ball bearing 97 does not rotate, and the rotary barrel 91 rotates relative to the bearing holder 93 in the range of 0 ° to 315 °, The outer race 97c of the ball bearing 97, the slide cams 31A to 31D, and the output shaft 12 rotate at a high speed relative to the bearing holder 93 by the driving force of the engine.

  Hereinafter, based on FIG. 51 to FIG. 61, the neutral gear is shifted up to the third gear through the first gear and the second gear, and then again through the second gear and the first gear. The operation when shifting down to the gear position will be described in detail.

  FIG. 51 shows a state in which the neutral gear stage is established. The first to fourth slide cams 31A to 31D are all in the left-right direction neutral position, and all the headballs 69 fall into the bottom of the cam grooves 31a. All the tail balls 70 ride on the cam grooves 64a, and each strut 71 swings clockwise to be disengaged from the driven gear. Therefore, in this state, the driven gear slips with respect to the output shaft 12 so that the rotation of the input shaft 11 is not transmitted to the output shaft 12.

  FIG. 52 shows a state in which the first gear is established. When the rotation angle of the rotary barrel 91 is 45 °, the first slide cam 31A is moved to the right by the guide groove 91a of the rotary barrel 91. The convex portion 31g of the cam groove 31a pushes up the head ball 69 of the first speed gear stage, and the tail ball 70 falls into the concave portion 64e of the first slide cam 31A, so that the strut 71 swings counterclockwise and is engaged. The rotation of the first-speed driven gear 21 is transmitted to the output shaft 12 via the strut 71, and the first-speed gear stage is established. At this time, the 2nd to 7th driven gears 22 to 27 are still in the disengaged state.

  FIG. 53 shows the process of shifting up from the first gear to the second gear. The rotational angle of the rotary barrel 91 is 70 °. At this time, the first slide cam 31A tries to return to the neutral position by the guide groove 91a of the rotary barrel 91, and the convex portion 31g of the cam groove 31a is retracted from below the headball 69 of the first speed gear stage. A cam groove 31a faces the lower side. However, the head ball 69 remains pushed up radially outward by centrifugal force, and the rotation of the first speed driven gear 21 is still transmitted to the output shaft 12 via the strut 71. That is, the first gear is in a one-way state, and transmission of driving force continues without interruption.

  As described above, when the first speed gear is in the one-way state and the driving force is transmitted, the strut 71 is restrained to the position swung counterclockwise, so that the tail ball 70 moves radially outward. Since the tail ball 70 is caught in the recess 64e of the cam groove 64a, the first slide cam 31A cannot move to the left and cannot return to the neutral position in a state where the actuator spring 34 is compressed. .

  At this time, the second slide cam 31B is moved to the right by the guide groove 91b of the rotary barrel 91, and the tail ball 70 falls into the recess 64e of the cam groove 64a of the second slide cam 31B. Eventually, when the notch 72 of the second speed driven gear 25 reaches the position of the strut 71, power transmission by the second speed shift stage is started. The second slide cam 31B is restrained from moving rightward while compressing the actuator spring 34 until the notch 72 of the second speed driven gear 25 reaches the position of the strut 71, and the notch 72 of the second speed driven gear 25 is restrained. As the second slide cam 31B moves to the right by the elastic force of the actuator spring 34 at the moment when the position reaches the strut 71, the second speed gear can be established without considering the drive timing of the actuator 92. .

  When the second gear is established in this way, the restraint of the strut 71 of the first gear is released and the tail ball 70 can move outward in the radial direction. The first slide cam 31A moves to the left by the generated force, returns to the neutral position, and the first gear is released. Thus, by moving the first slide cam 31A with a delay due to the elastic force of the compressed actuator spring 34, the movement amount of the first slide cam 31A by the actuator 92 is reduced and the axial dimension of the transmission T is reduced. Miniaturization can be achieved.

  In FIG. 54, the rotational angle of the rotary barrel 91 is 90 °, the convex portion 31g of the cam groove 31a of the second slide cam 31B that has moved right pushes up the headball 69, and the strut 71 swings counterclockwise. The state where the 2nd gear stage is established is shown.

  FIG. 55 shows the process of shifting up from the second gear to the third gear, and the rotational angle of the rotary barrel 91 is 115 °. At this time, the guide groove 91b of the rotary barrel 91 causes the second slide cam 31B to return to the neutral position, so that the convex portion 31g of the cam groove 31a is retracted from below the headball 69 of the second speed gear stage. A cam groove 31a faces the lower side. However, the head ball 69 remains pushed up radially outward by centrifugal force, and the rotation of the second speed driven gear 25 is still transmitted to the output shaft 12 via the strut 71. That is, the second gear is in a one-way state, and transmission of driving force continues without interruption.

  In this way, when the second gear is in the one-way state and transmitting the driving force, the strut 71 is restrained to the position swung counterclockwise, so that the tail ball 70 moves radially outward. Since the tail ball 70 is caught in the recess 64e of the cam groove 64a, the second slide cam 31B cannot move to the left and cannot return to the neutral position with the actuator spring 34 compressed. .

  At this time, the first slide cam 31A is moved to the left by the guide groove 91a of the rotary barrel 91, and the tail ball 70 falls into the recess 64e of the cam groove 64a of the first slide cam 31A. When the notch 72 of the third speed driven gear 22 reaches the position of the strut 71, power transmission by the third speed gear stage is started. Until the notch 72 of the third speed driven gear 22 reaches the position of the strut 71, the first slide cam 31A is restrained to move left while compressing the actuator spring 34, and the notch 72 of the third speed driven gear 22 is restricted. When the first slide cam 31A moves to the left by the elastic force of the actuator spring 34 at the moment when the position reaches the strut 71, the third gear can be established without considering the drive timing of the actuator 92. .

  When the third gear is established in this way, the restraint of the strut 71 of the second gear is released and the tail ball 70 can be moved radially outward. The second slide cam 31B moves to the left by the generated force, returns to the neutral position, and the second gear is released. Thus, by moving the second slide cam 31B with a delay due to the elastic force of the compressed actuator spring 34, the amount of movement of the second slide cam 31B by the actuator 92 is reduced, and the axial dimension of the transmission T is reduced. Miniaturization can be achieved.

  In FIG. 56, the rotational angle of the rotary barrel 91 is 135 °, the convex portion 31g of the cam groove 31a of the first slide cam 31A that has moved to the left pushes up the headball 69, and the strut 71 swings counterclockwise. A state in which the third gear is established is shown.

  The process of upshifting from the neutral gear stage to the third gear stage has been described above, but the process of upshifting from the third gear stage to the seventh gear stage is substantially the same as described above. A duplicate description is omitted. Hereinafter, the process of downshifting from the third gear to the neutral gear will be described.

  FIG. 57 shows the process of shifting down from the third gear to the second gear. The rotational angle of the rotary barrel 91 is 106.5 °. The first slide cam 31A returns to the neutral position by the first guide groove 91a of the rotary barrel 91, and the convex portion 31g of the cam groove 31a of the first slide cam 31A moves from the lower side to the right side of the head ball 69 of the third speed gear stage. When the head ball 69 falls into the cam groove 31 a and the cam groove 64 a pushes up the tail ball 70, the strut 71 swings clockwise and the first engagement surface 71 b is notched in the third speed driven gear 22. 72 is disengaged from the driving surface 72a of 72, and the third gear is released.

  At this time, the tail ball 70 of the second speed gear stage faces the recess 64e of the cam groove 64a, and the head ball 69 is urged radially outward by centrifugal force, but the notch 72 of the second speed driven gear 25 is strut 71. Since the position has not been reached, the second gear is not yet established. When the notch 72 of the second speed driven gear 25 reaches the position of the strut 71, the strut 71 swings clockwise to establish the second speed shift stage. Therefore, transmission of driving force is temporarily interrupted.

  FIG. 58 corresponds to a state in which the rotation angle of the rotary barrel 91 is 90 °, and the convex portion 31g of the cam groove 31a of the second slide cam 31B that has moved right pushes up the headball 69 and the strut 71 swings counterclockwise. And the 2nd gear stage has been established. The second slide cam 31B is prevented from moving right until the notch 72 of the second speed driven gear 25 reaches the position of the strut 71 and the second speed shift stage is established, but the actuator spring 34 is compressed. The shift in timing can be absorbed and the second gear can be established without considering the drive timing of the actuator 92.

  FIG. 59 shows the process of shifting down from the second gear to the first gear, and the rotational angle of the rotary barrel 91 is 61.5 °. The second slide cam 31B returns to the neutral position by the second guide groove 91b of the rotary barrel 91, and the convex portion 31g of the cam groove 31a of the second slide cam 31B moves from the lower side of the head ball 69 of the second speed gear stage to the left side. When the head ball 69 falls into the cam groove 31 a and the cam groove 64 a pushes up the tail ball 70, the strut 71 swings clockwise and the first engagement surface 71 b is notched in the second speed driven gear 25. 72, the second speed gear stage is released.

  At this time, the tail ball 70 of the first speed gear stage faces the concave portion 64e of the cam groove 64a, and the head ball 69 is urged radially outward by centrifugal force, but the notch 72 of the first speed driven gear 21 has the strut 71. Since the position has not been reached, the first gear is in an unestablished state. When the notch 72 of the first speed driven gear 21 reaches the position of the strut 71, the strut 71 swings in the clockwise direction to establish the first speed shift stage. Therefore, transmission of driving force is temporarily interrupted.

  FIG. 60 corresponds to a state in which the rotation angle of the rotary barrel 91 is 45 °, and the convex portion 31g of the cam groove 31a of the first slide cam 31A that has moved right pushes up the headball 69 and the strut 71 swings counterclockwise. And the 1st gear stage has shown the state established. The first slide cam 31A is prevented from moving rightward until the notch 72 of the first speed driven gear 21 reaches the position of the strut 71 and the first speed shift stage is established, but the actuator spring 34 is compressed. The first shift stage can be established without absorbing the timing shift and considering the drive timing of the actuator 92.

  FIG. 61 shows a state in which the neutral gear stage is established. This corresponds to a state in which the rotational angle of the rotary barrel 91 is 0 °, and the first slide cam 31A returns to the neutral position by the first guide groove 91a of the rotary barrel 91. The convex portion 31g of the cam groove 31a of the first slide cam 31A moves from the lower side to the left side of the head ball 69 of the first speed gear, the head ball 69 falls into the cam groove 31a, and the cam groove 64a is the tail ball. By pushing up 70, the strut 71 swings clockwise, the first engagement surface 71b is disengaged from the drive surface 72a of the notch 72 of the first speed driven gear 21, and the first speed shift stage is released.

  According to the third embodiment, basically the operational effects of the second embodiment can be achieved, and in addition to that, it is only necessary to arrange the driven gears with non-continuous gear positions as a set. Compared to the first and second embodiments in which the odd-numbered driven gear and the even-numbered driven gear are arranged together in order, the degree of freedom in the layout of the driven gear is greatly increased.

  In addition, since the driven gears that do not have continuous gear positions are arranged as a set, the operation for establishing the subsequent gear stage can be performed simultaneously in parallel while the release operation for the previous gear stage is being performed. Shifting is possible. If a driven gear with consecutive gear positions is set and arranged, the operation for establishing the subsequent gear stage will start after the completion of the release operation for the previous gear stage. In the meantime, there is a problem that transmission of driving force is interrupted.

  Furthermore, the slide cams 31A to 31C have only to be moved one stroke to the left and right (the slide cam 31D for the 7th speed gear stage is one stroke to the right), and the slide cams 31A to 31D are mutually connected. Since it is slidable by meshing with a comb, the axial dimension of the transmission T can be further shortened compared to the first and second embodiments.

  Moreover, since it is not necessary to arrange the cylinder 30 as an actuator inside the output shaft 12, not only can the diameter of the output shaft 12 be reduced, but also by arranging the actuator 92 outside the output shaft 12, The degree of freedom of selection can be increased.

  Since the inner race 97b and the outer race 97c of each bearing 97 supporting the first to fourth slide cams 31A to 31D are enlarged in the axial direction on the outer periphery of the bearing holder 93, the pin hole 97d formed in the inner race 97b is formed. The pin 98 can be connected to the rotary barrel 91, and the actuator spring 34 can be supported in the opening 97e formed in the outer race 97c. As a result, the number of parts can be greatly reduced, and the diameter of the output shaft 12 can be reduced.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, in the embodiment, among the input shaft 11 and the output shaft 12 of the transmission T, the driven gears 21 to 27 provided on the output shaft 12 are engaged and disengaged by the clutch mechanism 35. The provided drive gears 14 to 20 may be engaged / disengaged by the clutch mechanism 35 to perform the shift.

  Further, the number of gears is not limited to seven, and any number of gears can be employed.

1 is a longitudinal sectional view of a transmission according to a first embodiment. 2 enlarged view of FIG. 1 (sectional view taken along line 2-2 of FIG. 3) 3-3 sectional view of FIG. Sectional view along line 4-4 in FIG. Sectional view along line 5-5 in FIG. 6 direction arrow view of FIG. 7 is an enlarged perspective view of part 7 in FIG. Sectional view taken along line 8-8 in FIG. Sectional view taken along line 9-9 in FIG. Sectional view taken along line 10-10 in FIG. 11-11 sectional view of FIG. 12-12 sectional view of FIG. Perspective view of slide cam and slider Perspective view of strut, headball and tailball Action explanatory diagram showing the engaged state of the driven gear Action explanatory drawing showing the one-way state of the driven gear Action explanatory view showing the non-engagement state of the driven gear Diagram showing state when neutral gear is established The figure which shows the state at the time of 1st gear stage establishment Fig. 1 shows the state when shifting from 1st gear to 2nd gear (Part 1) Figure showing the state of upshifting from 1st gear to 2nd gear (Part 2) Figure showing the state of upshifting from 1st gear to 2nd gear (Part 3) The figure which shows the state at the time of 2nd gear stage establishment Diagram showing the state when shifting from 2nd gear to 3rd gear (Part 1) Diagram showing the state when shifting from 2nd gear to 3rd gear (Part 2) Diagram showing the state of upshifting from 2nd gear to 3rd gear (Part 3) The figure which shows the state at the time of 3rd gear stage establishment Diagram showing the state of downshift from 3rd gear to 2nd gear (Part 1) Diagram showing the state of downshift from 3rd gear to 2nd gear (2) The figure which shows the state at the time of 2nd gear stage establishment Diagram showing the state of downshift from 2nd gear to 1st gear (Part 1) The figure which shows the state at the time of downshift of 2nd speed-> 1st speed (the 2) The figure which shows the state at the time of 1st gear stage establishment Diagram showing state when neutral gear is established The figure corresponding to the said FIG. 2 based on 2nd Embodiment (35-35 sectional view taken on the line of FIG. 36). Sectional view taken along line 36-36 in FIG. Sectional view taken along line 37-37 in FIG. Sectional view taken along line 38-38 in FIG. Fig. 35 is an enlarged view of 39 part. Perspective view of slide cam Disassembled perspective view around the actuator spring The figure corresponding to the said FIG. 2 based on 3rd Embodiment (42-42 sectional view taken on the line of FIG. 43). Sectional view taken along line 43-43 in FIG. Sectional view taken along line 44-44 in FIG. Perspective view of slide cam 46 enlarged view of FIG. 47 arrow direction view of FIG. 48-48 sectional view of FIG. 48 is an exploded perspective view of 49 part of FIG. The figure which shows the guide groove of the rotary barrel Diagram showing state when neutral gear is established The figure which shows the state at the time of 1st gear stage establishment The figure which shows the state at the time of shift up from 1st speed → 2nd speed The figure which shows the state at the time of 2nd gear stage establishment The figure which shows the state at the time of upshift of 2nd speed-> 3rd speed The figure which shows the state at the time of 3rd gear stage establishment The figure which shows the state at the time of downshift of 3rd speed-> 2nd speed The figure which shows the state at the time of 2nd gear stage establishment The figure which shows the state at the time of downshift of 2nd gear → 1st gear The figure which shows the state at the time of 1st gear stage establishment Diagram showing state when neutral gear is established

Explanation of symbols

12 Output shaft (rotary shaft)
21 1-speed driven gear (gear)
22 3-speed driven gear (gear)
23 5-speed driven gear (gear)
24 7-speed driven gear (gear)
25 2-speed driven gear (gear)
26 4-speed driven gear (gear)
27 6-speed driven gear (gear)
28 Bush (Bearing member)
28 'ball bearing (bearing member)
31 Slide cam 35 Clutch mechanism 66 Strut storage groove 67 Head ball storage hole 68 Tail ball storage hole 69 Head ball 70 Tail ball 71 Strut 71b First engagement surface 71c Second engagement surface 71f Set ring engagement portion 72 Notch 73 Set ring

Claims (8)

A plurality of gears (21 to 27) are rotatably supported on the rotation shaft (12), and any one of the plurality of gears (21 to 27) is supported via the corresponding clutch mechanism (35). ) In a transmission capable of establishing a desired shift speed by being selectively coupled to
The clutch mechanism (35)
A strut accommodation groove (66) provided in the outer periphery of the rotary shaft (12) formed in a hollow;
A strut (71) supported in a swingable manner in the strut housing groove (66), and provided on the gear rotation direction delay side of the strut (71), and on the inner peripheral surface of the gear (21-27) A first engagement surface (71b) engageable with the notch (72) formed;
A second engagement surface (71c) that is provided on the gear rotation direction advance side of the strut (71) and engages with the strut accommodation groove (66);
According to the position of the slide cam (31) that is arranged to be movable in the axial direction inside the rotating shaft (12) and controls the swinging state of the strut (71),
An engagement state in which the first engagement surface (71b) of the strut (71) is forcibly projected into the notch (72) of the gear (21-27);
The first engagement surface (71b) of the strut (71) and the notch (72) of the rotation shaft (12) according to the relative rotation direction of the gear (21-27) with respect to the rotation shaft (12). ) And a one-way state to engage or disengage
A non-engagement state in which the first engagement surface (71b) of the strut (71) is forcibly retracted from the notch (72) of the gear (21-27);
A transmission characterized in that can be switched. The clutch mechanism (35)
A headball storage hole (67) communicating with the gear rotation direction delay side of the strut storage groove (66) and penetrating the rotation shaft (12) in the radial direction;
A headball (69) that is fitted in the headball housing hole (67) so as to be movable in the radial direction, and that can be brought into contact with the radial inner surface of the strut (71) on the delay side in the gear rotation direction;
A tail ball storage hole (68) communicating with the strut storage groove (66) in the gear rotation direction leading side and penetrating the rotation shaft (12) in the radial direction;
A tail ball (70) fitted in the tail ball storage hole (68) so as to be movable in the radial direction and capable of coming into contact with the radial inner surface of the strut (71) on the gear rotation direction advance side end;
The slide cam (31) can control the radial positions of the head ball (69) and the tail ball (70),
Depending on the position of the slide cam (31),
The head ball (69) is pushed outward in the radial direction while allowing the tail ball (70) to move inward in the radial direction, thereby causing the first engagement surface (71b) of the strut (71) to move to the gear. An engaged state for forcibly projecting into the notch (72) of (21-27);
By allowing the tail ball (70) and the head ball (69) to move radially inward, the first engagement surface (71b) of the strut (71) and the gears (21-27) A one-way state in which the notch (72) is engaged or disengaged;
By pushing the tail ball (70) radially outward while allowing the head ball (69) to move radially inward, the first engagement surface (71b) of the strut (71) is moved to the gear. The transmission according to claim 1, characterized in that it can be switched between a non-engaged state in which it is forcibly retracted from a notch (72) of (21-27).   During acceleration, the first engagement surface (71b) of the strut (71) and the notch (72) of the gear (21 to 27) are in surface contact with each other, and the second engagement surface ( The transmission according to claim 2, wherein 71c) and the strut accommodation groove (66) of the rotating shaft (12) are in surface contact.   The driving force during deceleration in the engaged state is that the notches (72) of the gears (21-27) through the strut (71), the headball (69), and the headball storage hole (67). Transmission according to claim 2, characterized in that it is transmitted to the rotary shaft (12) via   The transmission according to claim 2, wherein, when accelerating in the one-way state, the head ball (69) is urged to a radially outer position by its centrifugal force to maintain the engagement state. .   Each of the gears (21 to 27) is supported on the outer periphery of the rotating shaft (12) via a pair of bearing members (28, 28 ') at both ends in the axial direction, and the pair of bearing members (28, 28). The transmission according to any one of claims 1 to 5, characterized in that the clutch mechanism (35) is arranged in a space between ').   The transmission according to claim 6, wherein the bearing member (28) supports two adjacently arranged gears among the plurality of gears (21 to 27) at the same time.   In a state where the headball (69) and the tailball (70) are stored in the headball storage hole (67) and the tailball storage hole (68), respectively, the strut storage groove ( 66) housing the strut (71) and setting ring engaging portions (71f) projecting from both axial end surfaces of the strut (71) to the outer periphery of the output shaft (12) 73) The transmission according to any one of claims 2 to 5, wherein the transmission is held on an inner peripheral surface of 73).

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