JP2015081650A - Automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an automatic transmission in which a driving gear for starting, connected to an input shaft through a one-way clutch, is not rotated even when the input shaft is rotated by dragging torque generated in a hydraulic clutch.SOLUTION: A one-way clutch 34 disposed between an input shaft 2 and a driving gear 18 for starting, is disposed in a state that an engagement element 40 is movable in a wedge-shaped space 39 between an inner ring 35 and an outer ring 37. A retainer 41 for retaining the engagement element 40 is provided with an arm portion 47 projecting to a radial outer side, a sleeve 52 for the one-way clutch axially moved outside of the outer ring 37, is provided with a pressing portion 54, and the one-way clutch 34 is fastened when a pressure receiving portion 55 of the arm portion 47 is pressed by the pressing portion 54. When the pressing portion 54 is separated from the pressure receiving portion 55, the retainer 41 is rotated by a spring 43, and the one-way clutch 34 is made free. When a shift lever 57 is operated to a position excluding a running range in a state of stopping an output shaft 4, a sleeve 52 for the one-way clutch is moved to release the pressure receiving portion 55 from the pressing by the pressing portion 54.

Description

  The present invention relates to an automatic transmission in which a hydraulic clutch is arranged at an input end of a driving force, and is suitable for a dual clutch transmission in which two input shafts are individually connected to a driving source by a hydraulic clutch, for example.

  An example of such a dual clutch transmission is described in Patent Document 1 below. In this dual clutch transmission, a starting drive gear, a third speed drive gear, and a fifth speed drive gear are rotatably arranged on one first input shaft of two input shafts, and a second speed drive is driven on the other second input shaft. A gear, a 4-speed drive gear, a 6-speed drive gear, and a reverse drive gear are rotatably arranged. A driven gear that meshes with all the drive gears is fixed to the output shaft (an intermediate gear is interposed in the reverse drive gear). For example, a meshing clutch is disposed between the third speed driving gear and the fifth speed driving gear, between the second speed driving gear and the fourth speed driving gear, and between the sixth speed driving gear and the reverse driving gear. The meshing clutch has a sleeve that can move in the axial direction of each input shaft on which the corresponding drive gear is arranged, and by moving this sleeve in the axial direction of the corresponding input shaft, the gear shift selected by the shift lever is performed. The drive gear corresponding to the stage is connected to the corresponding input shaft. Accordingly, the hydraulic clutch of the input shaft on which the drive gear corresponding to the selected gear stage is arranged is engaged and the input shaft is connected to the engine that is the drive source. A one-way clutch is interposed between the starting drive gear and the first input shaft on which the starting drive gear is arranged.

JP 2012-117581 A

  By the way, also in the above-mentioned dual clutch transmission, the driving force is intermittently engaged / disengaged by engaging / disengaging a hydraulic clutch, as in a general automatic transmission or continuously variable transmission. Therefore, the one-way clutch interposed between the starting drive gear and the input shaft is in an engaged state in the driving force transmission direction. Therefore, for example, when lubricating oil is supplied to the hydraulic clutch at a low temperature, a driving force is transmitted, so-called drag torque is generated, the input shaft rotates, and the shift lever is in the N (neutral) position. There is a possibility that the starting drive gear may rotate.

  The present invention has been made by paying attention to the above-described problems. Even if the input shaft rotates with the drag torque generated in the hydraulic clutch even though the structure is simple, the input shaft is connected via the one-way clutch. It is an object of the present invention to provide an automatic transmission in which a starting drive gear connected to the vehicle does not rotate.

  In order to solve the above-described problems, an embodiment of the present invention provides an automatic transmission in which a hydraulic clutch is interposed at an input end portion of a driving force, an input shaft to which the driving force is input via the hydraulic clutch, and the input An output shaft disposed parallel to the shaft, a plurality of drive gears rotatably disposed on the input shaft, a plurality of driven gears meshed with the drive gear and fixed to the output shaft, A meshing clutch having a sleeve for connecting at least one of the drive gears to the input shaft, a starting drive gear of the plurality of drive gears, and a state in which the input shaft rotates integrally and freely A one-way clutch that switches to a rotatable state, an inner ring that is provided in the one-way clutch and is connected to the input shaft, an outer ring that is provided in the one-way clutch and that is outside the inner ring. An outer ring that is arranged and connected to the drive gear for starting, a wedge-shaped space provided between the inner ring and the outer ring, provided in the one-way clutch, and a ring-shaped holding provided in the one-way clutch An engagement element that is held by the cage and is movably disposed in the wedge-shaped space, an arm portion that is provided on the cage and projects radially outward from the cage, and interlocks with a sleeve of the meshing clutch A first position where the engaging element is not in contact with the outer ring by contacting a pressing portion that moves in the axial direction of the input shaft and a pressing portion that is provided in the arm portion and moves in the axial direction of the input shaft. The automatic transmission includes a pressure receiving portion that rotates the retainer at a second position where the engagement element can contact the inner ring and the outer ring.

  In addition, a one-way clutch sleeve that moves in the axial direction of the input shaft in conjunction with the mesh clutch sleeve is disposed on the outer peripheral portion of the outer ring, and the pressing portion is formed on the one-way clutch sleeve.

  A shift fork for moving the mesh clutch sleeve in the axial direction of the input shaft is fixed to a shifter shaft, and a one-way clutch fork for moving the one-way clutch sleeve in the axial direction of the input shaft Attached to the shifter shaft.

  The automatic transmission is a dual clutch transmission having two input shafts, and the starting drive gear, the third speed drive gear, and the fifth speed drive gear are rotatable on one of the two input shafts. The mesh clutch is disposed between the third speed drive gear and the fifth speed drive gear in the axial direction of the one input shaft, and the sleeve of the mesh clutch has an intermediate position, and the third speed drive gear is When the 3rd speed position connected to the input shaft and the 5th speed drive gear are moved to the 5th speed position connected to the input shaft and the sleeve of the meshing clutch is in the 5th speed position, the pressing portion is moved from the pressure receiving portion. The retainer is rotated by a spring so that the engagement element is disposed at the first position as it leaves, and the sleeve of the meshing clutch is at the intermediate position or 3 When in the position, the pressing portion pushes the pressure receiving portion so that the engaging element is disposed in the second position, the retainer is rotated, and the shift lever is in a position other than the travel range in a state where the output shaft is stopped. When operated to the position, the mesh clutch sleeve is moved to the fifth speed position.

  Thus, according to the embodiment of the invention, the hydraulic clutch is interposed at the input end of the input shaft. A one-way clutch is disposed between the input shaft and the starting drive gear. In this one-way clutch, an inner ring is connected to an input shaft, an outer ring is connected to a starting drive gear, and a wedge-shaped space is formed between the inner ring and the outer ring. In this wedge-shaped space, an engagement element held by a ring-shaped retainer is movably disposed. The cage is provided with an arm portion that protrudes radially outward. The arm portion contacts the pressing portion that moves in the axial direction of the input shaft in conjunction with the sleeve of the meshing clutch, and the first position where the engagement element does not contact the outer ring or the engagement element can contact the inner ring and the outer ring. A pressure receiving portion for rotating the cage is provided at the second position. When the engagement member of the one-way clutch is in the first position, the engagement member does not come into contact with the outer ring. Therefore, even if the input shaft rotates due to the drag torque generated in the hydraulic clutch, the start connected to the one-way clutch The rotation of the drive gear can be prevented. Therefore, even though the structure is simple, even if the input shaft is rotated by the drag torque generated by the hydraulic clutch, the starting drive gear connected to the input shaft via the one-way clutch can be prevented from rotating.

  A one-way clutch sleeve that moves in the axial direction of the input shaft in conjunction with the mesh clutch sleeve is disposed on the outer peripheral portion of the outer ring, and a pressing portion is formed on the one-way clutch sleeve. Therefore, the pressure receiving portion provided in the arm portion can be surely pressed by the pressing portion formed on the one-way clutch sleeve, and the cage can be rotated.

  A shift fork for moving the mesh clutch sleeve in the axial direction of the input shaft is fixed to the shifter shaft, and a one-way clutch fork for moving the sleeve of the one-way clutch in the axial direction of the input shaft is attached to the shifter shaft. It was. Therefore, the one-way clutch sleeve can be moved in the axial direction of the input shaft while simplifying the structure.

  The dual clutch transmission has two input shafts, one of the two input shafts has a starting drive gear, a third speed drive gear, and a fifth speed drive gear rotatably arranged in the axial direction of the input shaft. A meshing clutch is arranged between the third speed driving gear and the fifth speed driving gear. The engagement clutch sleeve is moved to the intermediate position, the third speed position, and the fifth speed position. When the engagement clutch sleeve is in the fifth speed position, the pressing portion is separated from the pressure receiving portion and the engagement element is disposed at the first position. The retainer is rotated by a spring. Further, when the mesh clutch sleeve is at the intermediate position or the third speed position, the pressing portion pushes the pressure receiving portion so that the engaging element is disposed at the second position, and the cage is rotated. When the shift lever is operated to a position other than the travel range with the output shaft stopped, the mesh clutch sleeve is moved to the fifth speed position. Therefore, even when the input shaft is rotated by the drag torque generated in the hydraulic clutch, it is possible to prevent the starting drive gear connected to the input shaft from rotating through the one-way clutch. Further, in the one-way clutch, the rotation speed of the output shaft increases, that is, the drag torque of the output shaft increases as the travel speed increases. However, when a 5-speed drive gear that is frequently used in high speed travel is selected. In addition, since the one-way clutch is placed in the first position by disposing the one-way clutch at the first position, the drive loss due to the one-way clutch can be reduced and the fuel consumption can be reduced.

It is a schematic block diagram of the dual clutch transmission which shows one Embodiment of the automatic transmission of this invention. FIG. 2 is an enlarged vertical sectional view of a main part of the one-way clutch in FIG. 1. It is a longitudinal cross-sectional view which shows the spring and arm part of the one-way clutch of FIG. FIG. 3 is an explanatory diagram of a state in which the engagement element is in a first position in the one-way clutch of FIG. 2. It is explanatory drawing of the state which has an engaging element in a 2nd position with the one-way clutch of FIG. FIG. 2 is a longitudinal sectional view in the vicinity of a starting drive gear to a meshing clutch of the dual clutch transmission of FIG. 1. FIG. 2 is a perspective view of a shifter shaft and a shift fork of the dual clutch transmission of FIG. 1. It is explanatory drawing of the sleeve for one-way clutches of FIG. 6, and the holder | retainer of a one-way clutch. It is explanatory drawing of the sleeve for one-way clutches of FIG. 6, and the holder | retainer of a one-way clutch. It is explanatory drawing of the positional relationship of the sleeve which makes an engaging element a 2nd position, and a holder | retainer. It is explanatory drawing of the position of an arm part when an engaging element exists in a 2nd position. It is explanatory drawing of the positional relationship of the sleeve which makes an engaging element a 1st position, and a holder | retainer. It is explanatory drawing of the position of an arm part when an engaging element exists in a 1st position.

  Next, an embodiment of an automatic transmission according to the present invention will be described with reference to the drawings. FIG. 1 is a schematic configuration diagram of a dual clutch transmission 1 which is an automatic transmission according to the present embodiment. This dual clutch transmission 1 is the same as that described in Patent Document 1, and has been previously proposed by the present applicant. The dual clutch transmission 1 includes a first input shaft 2 and a second input shaft 3 in parallel with the output shaft 4, and the first input shaft 2 is intermittently connected to an engine (not shown) via a first hydraulic clutch 5. The input shaft 3 is also intermittently connected to the engine via the second hydraulic clutch 6. The first hydraulic clutch 5 and the second hydraulic clutch 6 are connected to the engine via, for example, a chain (not shown). When the first hydraulic clutch 5 is fastened, the first input shaft 2 is connected to the engine, and the second hydraulic clutch When 6 is fastened, the second input shaft 3 is connected to the engine. Engagement / release control of each of the hydraulic clutches 5 and 6 is performed by a transmission control device described later. A differential drive gear 7 is attached to the first hydraulic clutch 5 and the second hydraulic clutch 6 side ends of the output shaft 4, and a differential device 9 is attached to a final reduction gear 8 that meshes with the differential drive gear 7. Yes. The differential device 9 is connected to the drive wheel 10 via a drive shaft.

  In the present embodiment, an odd-numbered gear train is disposed between the first input shaft 2 and the output shaft 4, and an even-numbered gear train is disposed between the second input shaft 3 and the output shaft 4. . The gear trains of the odd-numbered speed stages of the present embodiment are the first speed gear train 11, the third speed gear train 12, and the fifth speed gear train 13, and the gear trains of the even speed stages are the second speed gear train 14, 4th gear train 15 and 6th gear train 16. In the present embodiment, a reverse reverse gear train 17 is also disposed between the second input shaft 3 and the output shaft 4. From the first hydraulic clutch 5 side to the first input shaft 2, the fifth speed drive gear 20 of the fifth speed gear train 13, the third speed drive gear 19 of the third speed gear train 12, and the start of the first speed gear train 11 are started. Each drive gear 18 is rotatably mounted. On the other hand, on the second input shaft 3, from the second hydraulic clutch 6 side, the fourth speed drive gear 22 of the fourth speed gear train 15, the second speed drive gear 21 of the second speed gear train 14, and the sixth speed gear train 16 are provided. The 6th speed drive gear 23 and the reverse drive gear 24 of the reverse gear train 17 are rotatably mounted.

  The output shaft 4 includes, from the differential drive gear 7 side, a fourth-speed and fifth-speed driven gear that constitutes the fourth-speed gear train 15 and the fifth-speed gear train 13 and meshes with the fourth-speed drive gear 22 and the fifth-speed drive gear 20. 27, the second speed gear train 14 and the third gear train 12, and the second speed and third speed driven gear 26 meshing with the second speed drive gear 21 and the third speed drive gear 19, the first speed gear train 11 and The driven gear 25 for starting meshing with the driving gear 18 for starting, the sixth speed gear train 16 and the sixth speed driven gear 28 meshing with the sixth speed driving gear 23, the reverse gear train 17 are constructed, and the power is supplied from the reverse driving gear 24. The reverse driven gears 29 to which are transmitted are respectively fixed. An intermediate gear 30 is interposed between the reverse drive gear 24 and the reverse driven gear 29. Incidentally, the second-speed drive gear 21 and the third-speed drive gear 19 that mesh with the second-speed / third-speed driven gear 26 have the same modules, but different numbers of teeth. The 4-speed drive gear 22 and the 5-speed drive gear 20 that mesh with the 4-speed / 5-speed driven gear 27 also have the same module but different numbers of teeth.

  Between the 3rd speed drive gear 19 and the 5th speed drive gear 20, the 3rd speed drive gear 19 and the 1st input shaft 2 or the 5th speed drive gear 20 and the 1st input shaft are arranged on the outer periphery of the first input shaft 2. A third-speed / fifth-speed meshing clutch 31 for connecting the two is disposed. Similarly, between the 2nd speed drive gear 21 and the 4th speed drive gear 22, the 2nd speed drive gear 21 and the 2nd input shaft 3 or the 4th speed drive gear 22 and the 2nd input are arranged on the outer periphery of the second input shaft 3. A two-speed / four-speed meshing clutch 32 for connecting the shaft 3 is arranged. Similarly, between the 6-speed drive gear 23 and the reverse drive gear 24, on the outer periphery of the second input shaft 3, the 6-speed drive gear 23 and the second input shaft 3 or the reverse drive gear 24 and the second input shaft 3 are provided. A 6-speed / reverse meshing clutch 33 is connected. These meshing clutches 31 to 33 are dog-clutch type meshing clutches, for example, and by sliding the sleeve in the axial direction of the first input shaft 2 or the second input shaft 3, the drive gear on the moved side is moved. Connect to the input shaft.

  Therefore, when the second gear to the sixth gear or the reverse gear is selected by the shift lever, the meshing clutch sleeve of the corresponding gear is moved in the axial direction of the input shaft, and the corresponding driving gear is moved. To the input shaft. In this state, when the hydraulic clutch of the input shaft to which the corresponding drive gear is connected is fastened and connected to the engine, the driving force of the engine is transmitted to the output shaft 4 through the gear train composed of the corresponding drive gear and driven gear. Then, the drive wheel 10 can be driven via the differential device 9. A one-way clutch 34 described later is interposed between the starting drive gear 18 and the first input shaft 2. Incidentally, with the one-way clutch 34 engaged, for example, the third speed drive gear 19 or the fifth speed drive gear 20 is connected to the first input shaft 2, and the third speed gear train 12 or the fifth speed gear train 14 is operated. In this case, since the starting drive gear 18 rotates at a higher speed than the first input shaft 2, the one-way clutch 34 does not function.

  2 is an enlarged longitudinal sectional view of the main part of the one-way clutch 34 shown in FIG. 1, FIG. 3 is a longitudinal sectional view showing a spring and an arm part of the one-way clutch 34 shown in FIG. 2, and FIG. 4 is a one-way clutch shown in FIG. FIG. 5 is an explanatory view of a state where the engagement element is in the first position at 34, and FIG. 5 is an explanatory view of a state where the engagement element is in the second position in the one-way clutch 34 of FIG. The one-way clutch 34 has a structure similar to a rolling bearing as described in, for example, Japanese Patent Application Laid-Open No. 2001-50298. In the one-way clutch 34 of the present embodiment, the inner ring 35 is non-rotatably attached to the first input shaft 2 using spline coupling or the like. When viewed from the axial direction, the outer peripheral surface of the inner ring 35 is formed in a polygon, specifically, an octagon, and each plane constitutes a cam surface 36.

  A cylindrical outer ring 37 is disposed outside the inner ring 35. The outer ring 37 is connected to the starting drive gear 18 as shown in FIG. 6, for example. Since the inner peripheral surface 38 of the cylindrical outer ring 37 is an arcuate curved surface, a wedge-shaped space 39 having narrow ends in the circumferential direction is formed between the cam surface 36 of the inner ring 35 and the inner peripheral surface 38 of the outer ring 37. The Since there are eight cam surfaces 36 of the inner ring 35 of this embodiment, there are also eight wedge-shaped spaces 39 formed between the inner peripheral surface 38 of the outer ring 37. In each of the eight wedge-shaped spaces 39, an engaging element 40 made of a roller is disposed. All the engagement elements 40 are held by a ring-shaped retainer 41 that is continuous in the circumferential direction so that the distance between them is constant, and each engagement element 40 is accommodated in a pocket 42 of the retainer 41. .

  For example, as shown in FIG. 4, when the engagement element 40 is in the wedge-shaped space 39 and is located at the center in the circumferential direction of the cam surface 36, the engagement element 40 is located between the engagement element 40 and the inner peripheral surface 38 of the outer ring 37. There is a small gap a, and the outer ring 37 and the inner ring 35 are in a so-called free state where they are not restrained from each other. This position is defined as the first position. On the other hand, when the retainer 41 is rotated in the circumferential direction from this state, for example, as shown in FIG. 5, when the engaging element 40 is in the wedge-shaped space 39 and positioned at both circumferential ends of the cam surface 36, The engagement element 40 contacts both the inner peripheral surface 38 of the outer ring 37 and the cam surface 36 of the inner ring 35. At this time, the wedge-shaped space 39 between the cam surface 36 and the inner peripheral surface 38 becomes narrower toward both ends in the circumferential direction of the cam surface 36, so that the engagement element 40 is placed in the wedge-shaped space 39 of the inner peripheral surface 38 and the cam surface 36. The outer ring 37 and the inner ring 35 are brought into a fastened state through the engagement element 40. This position is defined as the second position.

  The one-way clutch 34 is provided with a spring 43 that rotates the retainer 41 so as to automatically return the engagement element 40 to the first position. The spring 43 is formed, for example, by bending a leaf spring in a ring shape, and the curved portion is fitted and fixed in the groove portion of the inner ring 35. The spring 43 is formed with, for example, an operating portion 44 in which both end portions of the leaf spring protrude outward in the radial direction. The operating portion 44 passes through the notched portion 45 of the inner ring 35 and the notched portion of the retainer 41. The portion 46 is engaged. Therefore, for example, when the force that maintains the engagement element 40 in the second position by rotating the retainer 41 in one circumferential direction is released, the retainer 41 is rotated in the reverse direction of the circumferential direction by the spring 43. The combination 40 is moved to the first position and held. On the other hand, in order to rotate the retainer 41 in the circumferential direction and maintain the engaging element 40 in the second position, the retainer 41 is provided with an arm portion 47 that protrudes radially outward.

  FIG. 6 is a longitudinal sectional view of the vicinity of the starting drive gear 18 to the third and fifth meshing clutch 31 of the dual clutch transmission 1 of FIG. As shown in the figure, for example, the first input shaft 2 and the output shaft 4 are rotatably supported by the transmission case via bearings 48, respectively. As described above, for example, a dog clutch or the like is used in the meshing clutch represented by the 3-speed / 5-speed meshing clutch 31, and in this type of meshing clutch, the sleeve is moved in the axial direction to fasten the clutch. Or cancel. For example, in the third and fifth meshing clutch 31 shown in FIG. 6, the meshing clutch sleeve 49 is moved in the axial direction of the first input shaft 2 to connect the three-speed drive gear 19 to the first input shaft 2. The fifth speed drive gear 20 is connected to the first input shaft 2.

  When the mesh clutch sleeve 49 is moved in the axial direction of the first input shaft 2, a shift fork 50 that is also used in a manual transmission or the like is used. The shift fork 50 is connected to a shifter shaft 51, and the shifter shaft 51 is moved in the axial direction of the first input shaft 2 or in a direction parallel to the axial direction of the first input shaft 2 by an actuator (not shown). Thus, the shift fork 50 is moved in the axial direction of the first input shaft 2, and the mesh clutch sleeve 49 is moved in the axial direction of the first input shaft 2 accordingly. FIG. 7 is a perspective view of the shifter shaft 51 and the shift fork 50 of the dual clutch transmission 1 of FIG. In this embodiment, a one-way clutch sleeve 52 is provided on the outer peripheral portion of the outer ring 37 in order to operate the arm portion 47 provided on the retainer 41 of the one-way clutch 34.

  The one-way clutch sleeve 52 is movable in the axial direction of the first input shaft 2 by a spline formed on the outer peripheral surface of the outer ring 37, similarly to the mesh clutch sleeve 49. A one-way clutch fork 53 is attached to the shifter shaft 51 in order to move the one-way clutch sleeve 52 in the axial direction of the first input shaft 2. Accordingly, when the shift fork 50 and the shifter shaft 51 are moved to the right in FIG. 6 in order to connect the 5-speed drive gear 20 to the first input shaft 2 by the 3-speed / 5-speed meshing clutch 31, the one-way clutch is accordingly moved. The sleeve 52 also moves to the right in FIG. This position is defined as the fifth speed position. Similarly, when the shift fork 50 and the shifter shaft 51 are moved to the left in FIG. 6 in order to connect the 3-speed drive gear 19 to the first input shaft 2 by the 3-speed / 5-speed meshing clutch 31, the one-way clutch is accordingly moved. The sleeve 52 also moves to the left in FIG. This position is defined as the 3rd speed position. An intermediate position between the fifth speed position and the third speed position is defined as an intermediate position.

  8 and 9 are explanatory views of the one-way clutch sleeve 52 and the retainer 41 of the one-way clutch 34 shown in FIG. A pressing portion 54 protruding in the axial direction is provided on the outer peripheral surface of the one-way clutch sleeve 52 of the present embodiment. On the other hand, a pressure receiving portion 55 is formed at the protruding end portion of the arm portion 47 protruding outward in the radial direction of the cage 41. The pressing portion 54 and the pressure receiving portion 55 are formed with inclined surfaces 56 that can come into close contact with each other. For example, when the one-way clutch sleeve 52 is moved in the axial direction, the inclined surface 56 comes into contact with the inclined surface 56 of the pressure receiving portion 55 when the one-way clutch sleeve 52 moves in the axial direction. With the movement in the axial direction, the retainer 41 provided with the pressure receiving portion 55, that is, the arm portion 47 has a function of rotating in the circumferential direction.

  In the present embodiment, as shown in FIG. 8, when the one-way clutch sleeve 52 and the retainer 41 are in substantially the same position in the axial direction, the inclined surface 56 of the pressing portion 54 does not contact the inclined surface 56 of the pressure receiving portion 55. . In this state, the rotational force in the circumferential direction of the arm portion 47, that is, the retainer 41 by the pressing portion 54 does not act, so the engagement element 40 held by the retainer 41 is in the first position, that is, the one-way clutch 34 is free. Maintained in a state. On the other hand, as shown in FIG. 9, when the one-way clutch sleeve 52 and the retainer 41 are in a position shifted in the axial direction, the inclined surface 56 of the pressing portion 54 contacts the inclined surface 56 of the pressure receiving portion 55, and the arm portion 47 and the retainer 41 are rotated in the circumferential direction. At this time, the engaging element 40 held by the retainer 41 is in the second position, that is, the one-way clutch 34 is engaged. In this embodiment, the position of the one-way clutch sleeve 52 in FIG. 8, that is, the first position of the engagement element 40 is the one when the shifter shaft 51 and the shift fork 50 are in the fifth speed position, and the one-way clutch in FIG. The position of the clutch sleeve 52, that is, the second position of the engagement element 40 is the position when the shifter shaft 51 and the shift fork 50 are in the intermediate position or the third speed position.

  Therefore, for example, as shown in FIG. 10, when the drive position is selected by the shift lever 57, the actuator 59 is controlled by the transmission control device 58, and the one-way clutch fork 53 is illustrated via the shifter shaft 51. It is moved to the third speed position in the middle of the figure (same as the middle of the figure in FIG. 6). Accordingly, when the one-way clutch sleeve 52 is moved in the middle of the drawing, the pressure receiving portion 55 is pressed by the pressing portion 54, and the arm portion 47 and the retainer 41 are rotated counterclockwise in FIG. Therefore, the engagement element 40 is moved to the second position in FIG. 11, and the one-way clutch 34 is in an engaged state. On the other hand, as shown in FIG. 12, for example, when the neutral position is selected by the shift lever 57, the actuator 59 is controlled by the transmission control device 58, and the one-way clutch fork 53 is illustrated via the shifter shaft 51. 12 is moved to the fifth speed position on the right side of the figure (same as the right side of the figure in FIG. 6). Accordingly, when the one-way clutch sleeve 52 is moved to the right in the figure, the pressure receiving portion 55 is released from being pressed by the pressing portion 54, and the retainer 41 is rotated in the clockwise direction in FIG. Therefore, the engagement element 40 is moved to the first position in FIG. 13, and the one-way clutch 34 is in a free state.

  In this embodiment, when the output shaft 4 is stopped and the shift lever 57 selects a neutral position that is a gear position other than the travel range, the transmission control device 58 controls the actuator 59. The one-way clutch fork 53 is moved to the fifth speed position on the right side of FIG. 12 (the same as the right side of FIG. 6) via the shifter shaft 51. Therefore, for example, when a shift position other than the travel range such as a neutral position is selected by the shift lever 57, the one-way clutch 34 is maintained in a free state. Accordingly, for example, when the first hydraulic clutch 5 generates drag torque and the first input shaft 2 rotates, for example, when the vehicle is cold, the start drive gear 18 is not rotated. Do not run.

  As described above, in the automatic transmission according to the present embodiment, the first hydraulic clutch 5 is interposed at the input end of the first input shaft 2. A one-way clutch 34 is disposed between the first input shaft 2 and the starting drive gear 18. In the one-way clutch 34, an inner ring 35 is connected to the first input shaft 2, an outer ring 37 is connected to the starting drive gear 18, and a wedge-shaped space 39 is formed between the inner ring 35 and the outer ring 37. In the wedge-shaped space 39, an engaging element 40 held by a ring-shaped holder 41 is movably disposed. The cage 41 is provided with an arm portion 47 that projects outward in the radial direction. The arm portion 47 is in contact with the pressing portion 54 that moves in the axial direction 2 of the first input shaft in conjunction with the mesh clutch sleeve 49, so that the engagement element 40 does not contact the outer ring 37. A pressure receiving portion 55 that rotates the retainer 41 is provided at a second position where the joint 40 can contact the inner ring 35 and the outer ring 37. When the engagement element 40 of the one-way clutch 34 is in the first position, the engagement element 40 does not come into contact with the outer ring 37. Therefore, there is a case where the first input shaft 2 is rotated by the drag torque generated in the first hydraulic clutch 5. However, it is possible to prevent the starting drive gear 18 connected to the one-way clutch 34 from rotating. Therefore, even if the first input shaft 2 is rotated by the drag torque generated in the first hydraulic clutch 5 while having a simple structure, the starting drive gear connected to the first input shaft 2 via the one-way clutch 34 is achieved. It can be set as the structure where 18 does not rotate.

  A one-way clutch sleeve 52 that moves in the axial direction of the first input shaft 2 in conjunction with the mesh clutch sleeve 49 is disposed on the outer periphery of the outer ring 37, and a pressing portion 54 is formed on the one-way clutch sleeve 52. Therefore, the pressure receiving portion 55 provided on the arm portion 47 can be reliably pressed by the pressing portion 54 formed on the one-way clutch sleeve 52, and the cage 41 can be rotated.

  Further, a shift fork 50 for moving the meshing clutch sleeve 49 in the axial direction of the first input shaft 2 is fixed to the shifter shaft 51, and the one-way clutch sleeve 52 is moved in the axial direction of the first input shaft 2. The one-way clutch fork 53 was attached to the shifter shaft 51. Therefore, the one-way clutch sleeve 52 can be moved in the axial direction of the first input shaft 2 while simplifying the structure.

  Further, the first input shaft 2 and the second input shaft 3 are provided as a dual clutch transmission, and one of the two input shafts has a starting drive gear 18, a third speed drive gear 19, and a fifth speed drive. The gear 20 is rotatably arranged, and the third-speed / fifth-speed meshing clutch 31 is disposed between the third-speed drive gear 19 and the fifth-speed drive gear 20 in the axial direction of the first input shaft 2. The meshing clutch sleeve 49 of the meshing clutch 31 is moved to the intermediate position, the third speed position, and the fifth speed position. When the meshing clutch sleeve 49 is in the fifth speed position, the pressing portion 54 is separated from the pressure receiving portion 55. The retainer 41 is rotated by the spring 43 so that the engagement element 40 is disposed at the first position. When the mesh clutch sleeve 49 is in the intermediate position or the third speed position, the pressing portion 54 pushes the pressure receiving portion 55 so that the engaging element 40 is disposed in the second position, and the retainer 41 is rotated. When the shift lever 57 is operated to a position other than the travel range with the output shaft 4 stopped, the mesh clutch sleeve 49 is moved to the fifth speed position. Therefore, even when the first input shaft 2 is rotated by the drag torque generated in the first hydraulic clutch 5, the start drive gear 18 connected to the first input shaft 2 is rotated through the one-way clutch 34. Can be prevented. In the one-way clutch 34, the rotational speed of the output shaft 4 increases, that is, the drag torque of the output shaft 4 increases as the travel speed increases. However, the 5-speed drive gear 19 that is frequently used in high speed travel is selected. In such a case, the engagement member 40 of the one-way clutch 34 is disposed at the first position so that the one-way clutch 34 is in a free state. Therefore, driving loss due to the one-way clutch 34 can be reduced and fuel consumption can be reduced. .

1 is a dual clutch transmission 2 is a first input shaft 3 is a second input shaft 4 is an output shaft 5 is a first hydraulic clutch 6 is a second hydraulic clutch 7 is a differential drive gear 8 is a final reduction gear 9 is a differential device 10 is driven Wheel 11 is a first gear train 12 is a third gear train 13 is a fifth gear train 14 is a second gear train 15 is a fourth gear train 16 is a sixth gear train 17 is a reverse gear train 18 is The starting drive gear 19 is a 3-speed drive gear 20 is a 5-speed drive gear 21 is a 2-speed drive gear 22 is a 4-speed drive gear 23 is a 6-speed drive gear 24 is a reverse drive gear 25 is a start driven gear 26 is a 2-speed drive gear 3-speed driven gear 27 is 4-speed / 5-speed driven gear 28 is 6-speed driven gear 29 is reverse driven gear 30 is intermediate gear 31 is 3-speed-5-speed meshing clutch 32 is 2-speed 4-speed meshing clutch 3 is a 6-speed / reverse meshing clutch 34 is a one-way clutch 35 is an inner ring 36 is a cam surface 37 is an outer ring 38 is an inner peripheral surface 39 is a wedge-shaped space 40 is an engagement element 41 is a retainer 42 is a pocket 43 is a spring 44 is an operation unit 45 Is a notch part 46 is a notch part 47 is an arm part 48 is a bearing 49 is a meshing clutch sleeve 50 is a shift fork 51 is a shifter shaft 52 is a one-way clutch sleeve 53 is a one-way clutch fork 54 is a pressing part 55 is a pressure receiving part 56 is an inclined surface 57 is a shift lever 58 is a transmission control device 59 is an actuator

Claims (4)

In an automatic transmission in which a hydraulic clutch is interposed at the input end of the driving force,
An input shaft to which driving force is input via the hydraulic clutch;
An output shaft arranged parallel to the input shaft;
A plurality of drive gears rotatably disposed on the input shaft;
A plurality of driven gears meshed with the drive gear and fixed to the output shaft;
A meshing clutch having a sleeve for connecting at least one of the drive gears to the input shaft;
A one-way clutch that switches between a driving gear for starting out of the plurality of driving gears and a state in which the input shaft rotates integrally and a state in which the input shaft can rotate freely;
An inner ring provided in the one-way clutch and coupled to the input shaft;
An outer ring provided on the one-way clutch, disposed on the outer side of the inner ring and coupled to the driving gear for starting;
A wedge-shaped space provided in the one-way clutch and formed between the inner ring and the outer ring;
An engagement element provided in the one-way clutch, held by a ring-shaped retainer and movably disposed in the wedge-shaped space;
An arm portion provided on the retainer and projecting radially outward from the retainer;
A pressing portion that moves in the axial direction of the input shaft in conjunction with a sleeve of the meshing clutch;
A second position provided on the arm portion and in contact with a pressing portion that moves in the axial direction of the input shaft so that the engagement element does not contact the outer ring, or a second position where the engagement element can contact the inner ring and the outer ring. An automatic transmission comprising a pressure receiving portion for rotating the retainer at a position. A one-way clutch sleeve that moves in the axial direction of the input shaft in conjunction with the mesh clutch sleeve is disposed on the outer periphery of the outer ring,
The automatic transmission according to claim 1, wherein the pressing portion is formed on the one-way clutch sleeve. A shift fork for moving the mesh clutch sleeve in the axial direction of the input shaft is fixed to the shifter shaft;
3. The automatic transmission according to claim 2, wherein a one-way clutch fork for moving the one-way clutch sleeve in the axial direction of the input shaft is attached to the shifter shaft. The automatic transmission is a dual clutch transmission having two input shafts;
The starting drive gear, the 3-speed drive gear, and the 5-speed drive gear are rotatably arranged on one of the two input shafts,
The mesh clutch is disposed between the third speed drive gear and the fifth speed drive gear in the axial direction of the one input shaft;
The mesh clutch sleeve is moved to an intermediate position, a third speed position connecting the third speed drive gear to the input shaft, and a fifth speed position connecting the fifth speed drive gear to the input shaft;
When the mesh clutch sleeve is in the fifth speed position, the retainer is rotated by a spring so that the pressing portion is separated from the pressure receiving portion and the engaging element is disposed in the first position;
When the mesh clutch sleeve is in the intermediate position or the third speed position, the pressing portion pushes the pressure receiving portion so that the retainer is rotated so that the engagement element is disposed in the second position;
The automatic transmission according to claim 3, wherein when the shift lever is operated to a position other than a travel range with the output shaft stopped, the sleeve of the meshing clutch is moved to the fifth speed position. .

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