JP2013127299A - Automatic transmission shift device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an automatic transmission shift device with a gear support structure having low cost and lightweight.SOLUTION: An automatic transmission shift device comprises: a case 111 in which an upper case 112 is fixed to a bottom wall 113 of a transmission case 11; a motor 114; a pinion shaft 116 having a pinion 116a at its end; a reduction gear mechanism 118 having a reduction gear; a support plate 120 which supports the lower face of the reduction gear from a lower part in the gravity direction so that the reduction gear may not fall from an opening of the upper case 112 when attaching the upper case 112 assembled with the motor 114, the pinion shaft 116 and the reduction gear mechanism 118 to the peripheral wall of the transmission case 11; a fixed part 122 to which the support plate 120 is screwed; a rotation regulation part 124 which abuts on the support plate 120 and regulates the rotation of the support plate 120; a folk shaft 95 engaged with the pinion 116a; and a shift folk 91 fixed to the folk shaft 95.

Description

  The present invention relates to a shift device for an automatic transmission.

2. Description of the Related Art Conventionally, several automatic transmissions for vehicles such as automobiles that have been automated based on a gear-type manual transmission that is considered to have good power transmission efficiency have been proposed. For example, in an automatic transmission disclosed in Patent Document 1, a shift actuator mechanism 2 is attached to a peripheral wall of a housing 5 incorporating a speed change mechanism. The shift actuator mechanism 2 operates the shift and select shaft 24 in the axial direction and the rotational axis direction by two mounted electric motors (select motor 60 and shift motor 25), respectively. Depending on the operation in the axial direction, the shift and select shaft 24 is engaged with a target fork shaft among a plurality of fork shafts arranged in the housing 5. Further, depending on the operation in the rotation axis direction, the engaged fork shaft is moved in the axial direction, and the sleeve of the gear shift clutch connected to the fork shaft is operated to connect / disconnect a predetermined gear stage.
Between the two electric motors and the shift and select shaft 24, a gear group 26 composed of a plurality of reduction gears for reducing the rotational speed of each motor is interposed. Each reduction gear has a rotation shaft, and both ends of each rotation shaft are rotatably supported by the housing 5 and the case 22 of the shift actuator mechanism 2 in a state where the shift actuator mechanism 2 is attached to the housing 5. The shift actuator mechanism 2 configured in this manner is generally disposed above the housing 5 in order to prevent failure due to collision with water splashes, pebbles and the like. For this reason, when the shift actuator mechanism 2 is assembled to the housing 5, the case 22 is assembled with the opening 20 of the case 22 opened downward in the direction of gravity, and the gear group 26 is screwed by a bolt so as not to fall from the opening 20. It is supported by a worn gear support plate.

Japanese Patent Laid-Open No. 2004-347094

  However, since the conventional technique of Patent Document 1 configured as described above has both the shift mechanism and the select mechanism, the gear group 26 has a large number of reduction gears. For this reason, since there are many reduction gears which the gear support plate should support so that it may not fall from the open port 20, a gear support plate will become large and a weight will also increase. When such a gear support plate receives vibration from an electric motor or the like, for example, the gear support plate is provided with a large rotational biasing force according to a large shape and weight, and is a screw that is rotated and screwed around a screwed portion. There is a risk of loosening.

  For this reason, in the prior art, in order to prevent rotation, for example, when the gear support plate is fixed at two or more points, or when the gear support plate is fixed at one point, a pawl is provided on the gear support plate. Further, it is necessary to take measures such as providing a strong rib on the case for bringing the pawl portion into contact with each other to surely suppress the rotation. For this reason, there exists a possibility that component cost may become high while weight increase.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a shift device for an automatic transmission provided with a low-cost and lightweight gear support structure.

  In order to solve the above-mentioned problem, the invention of the shift device for an automatic transmission according to claim 1 is characterized in that a part of the peripheral wall of the transmission case is a bottom wall and the upper case is fixed to the bottom wall at the peripheral edge of the opening. A case in which a gear chamber is formed, a motor supported in the case, a pinion shaft that is removably supported on the ceiling wall and the bottom wall of the upper case, and a pinion is formed at the end. A reduction gear mechanism having a reduction gear interposed between the output shaft of the motor and the pinion shaft and fixed to the pinion shaft; and the upper case in which the motor, the pinion shaft and the reduction gear mechanism are assembled. Is attached to the peripheral wall of the transmission case, the reduction gear and the gear meshing with the reduction gear fall from the opening of the upper case. A support plate that supports the reduction gear and the lower surface of the gear that meshes with the reduction gear from below in the direction of gravity, and a support surface that is provided in the upper case and is screwed to the support plate is the peripheral edge of the opening. A fixing portion formed at a predetermined position with respect to the lower surface, and the support having a rotation shaft at the center of a screwed portion that is provided in the upper case and contacts the support plate and screws the support plate to the fixing portion. A rotation restricting portion for restricting the rotation of the plate, a fork shaft having a rack meshing with the pinion and supported so as to be movable in the axial direction in the transmission case, and a shift fork fixed to the fork shaft. Prepare.

  According to a second aspect of the present invention, there is provided the shift device for an automatic transmission according to the first aspect, wherein the rotation restricting portion is provided on at least one of the motor supporting portion and the inner peripheral wall of the upper case in the upper case.

  According to a third aspect of the present invention, there is provided the shift device for an automatic transmission according to the first or second aspect, wherein the reduction gear is provided on the bottom wall when the upper case is attached to the peripheral wall of the transmission case. It is supported by an annular support portion that supports the pinion shaft and is separated from the support plate.

  According to the first aspect of the present invention, the shift device does not have a selection mechanism, and the fork shaft is operated in the axial direction only by the rotation operation of the pinion shaft, and the shift stage is switched. When the shift device is attached to the peripheral wall of the transmission case, a support plate is provided so that the reduction gear and the gear meshing with the reduction gear do not fall from the opening directed downward in the gravitational direction. The support plate is screwed and fixed to a fixing portion in the upper case, and is also in contact with a rotation restricting portion provided in the upper case to restrict rotation about the screwed portion center as a rotation axis. At this time, since the shift device does not have a selection mechanism, the reduction gear mechanism has a simple configuration, and the support plate can be made small and light. Thereby, a rotation control part can also be formed simply and a low-cost and lightweight shift device can be realized.

  According to the invention of the shift device for an automatic transmission according to claim 2, since the rotation restricting portion is provided on at least one of the motor support portion and the inner peripheral wall of the upper case, the shape in the upper case is reduced. There is no need to change, and a low-cost and lightweight shift device can be realized.

  According to the invention of the shift device for an automatic transmission according to claim 3, in a state where the upper case is attached to the peripheral wall of the transmission case, the reduction gear is provided on the annular support portion that is provided on the bottom wall and supports the pinion shaft. By being supported, it is separated from the support plate. Thus, when the shift device is operated, the reduction gear can be operated satisfactorily without receiving rotational resistance from the support plate.

FIG. 3 is a perspective view of a transmission case 11 and a clutch housing 12 of the case 10 as viewed from the side. It is 2-2 sectional drawing in FIG. 1, and is the figure by which the shift apparatus which concerns on 1st Embodiment was mounted. It is a skeleton figure which shows the whole structure of a transmission. FIG. 4 is a cross-sectional view taken along 4-4 in FIG. 2. It is 5-5 sectional drawing in FIG. FIG. 6 is a cross-sectional view taken along 6-6 in FIG. 5. It is sectional drawing which cut | disconnected the shift apparatus which concerns on 2nd Embodiment similarly to FIG. It is 8-8 sectional drawing in FIG.

  Hereinafter, a first embodiment of an automatic transmission to which a shift device embodying the present invention is applied will be described with reference to FIGS. As shown in FIGS. 1 to 3, the automatic transmission 1 according to the first embodiment is a seven-speed forward dual clutch automatic transmission, and in the axial direction within the case 10, a first input shaft 21, A second input shaft 22, a first counter shaft 31 and a second counter shaft 32 are provided. Also, in the case 10, there are a dual clutch 40 (see FIG. 3), drive gears 51 to 57 for each gear, final reduction drive gears 58 and 68, driven gears 61 to 67 for each gear, a reverse gear 70, and a ring gear 80. It has. Hereinafter, the same axial direction as the first input shaft 21, the second input shaft 22, the first auxiliary shaft 31, and the second auxiliary shaft 32 is referred to as an input axis direction. In the text, the term “upper and lower” without any special explanation means the upper and lower sides in the direction of gravity.

  As shown in FIG. 1, the case 10 includes a transmission case 11 (corresponding to the transmission case of the present invention) and a clutch housing 12. As shown in FIG. 2, the transmission case 11 drives the first to fourth shift clutches 101 to 104 shown in FIG. 3 provided for the first countershaft 31 and the second countershaft 32, respectively. Four shift devices 110 according to the present invention for disengaging and switching stages are provided. In FIG. 2, two shift devices 110 are shown as representatives.

  The clutch housing 12 has an end face that faces the end face of the transmission case 11, and is fixed to the transmission case 11 by bolt fastening. The clutch housing 12 supports each shaft by a plurality of bearings and accommodates a dual clutch 40 therein.

  The first input shaft 21 is rotatably supported with respect to the transmission case 11 and the clutch housing 12 by a bearing. Further, a portion for supporting the bearing and a plurality of external splines are formed on the outer peripheral surface of the first input shaft 21. A first speed drive gear 51 and a third speed drive gear 53 are directly formed on the first input shaft 21. The fifth speed drive gear 55 and the seventh speed drive gear 57 are press-fitted by spline fitting into external splines formed on the outer peripheral surface of the first input shaft 21. Further, a connecting portion that is connected to the first clutch 41 of the dual clutch 40 is formed at the end of the first input shaft 21.

  The second input shaft 22 is formed in a hollow shaft shape, is rotatably supported on the outer periphery of a part of the first input shaft 21 via a plurality of bearings, and the transmission case 11 and the clutch housing 12 are supported by the bearings. Is supported rotatably. That is, the second input shaft 22 is disposed so as to be rotatable relative to the first input shaft 21 concentrically. Similarly to the first input shaft 21, a portion that supports the bearing and a plurality of external gears are formed on the outer peripheral surface of the second input shaft 22. A second speed drive gear 52, a fourth speed drive gear 54 and a sixth speed drive gear 56 are formed on the second input shaft 22. Further, a connecting portion that is connected to the second clutch 42 of the dual clutch 40 is formed at the end of the second input shaft 22.

  The first countershaft 31 is rotatably supported with respect to the transmission case 11 and the clutch housing 12 by a bearing, and is disposed in parallel to the first input shaft 21 in the transmission case 11. A final reduction drive gear 58 is formed on the outer peripheral surface of the first countershaft 31, and a portion for supporting the bearing and a plurality of external splines are formed. The clutch hubs 201 of the first and third shift clutches 101 and 103 are press-fitted into the external splines of the first countershaft 31 by spline fitting.

The shift devices 110 that drive the first and third shift clutches 101 and 103 are fixed to the peripheral wall of the upper part of the transmission case 11 near the first and third shift clutches 101 and 103, respectively (see FIG. 2). Only the shift device 110 that drives the third shift clutch 103 is shown). The final reduction drive gear 58 meshes with a ring gear 80 of a differential (differential mechanism). The ring gear 80 is arranged on the internal combustion engine E / G side in the axial direction among the gears arranged in the transmission case 11.
Further, the first countershaft 31 is formed with a support portion that supports the first-speed driven gear 61, the third-speed driven gear 63, the fourth-speed driven gear 64, and the reverse gear 70 so as to be freely rotatable.

The first speed driven gear 61 is always meshed with a first speed drive gear 51 formed on the first input shaft 21. Further, the third speed driven gear 63 is always meshed with a third speed drive gear 53 formed on the first input shaft 21.
The 4-speed driven gear 64 is always meshed with the 4-speed drive gear 54 formed on the second input shaft 22, and the reverse gear 70 is supported on the second output shaft 31 so as to be freely rotatable. It is always meshed with a small diameter gear 62 a formed integrally with 62. Thus, when the second speed drive gear 52 of the second input shaft 22 meshed with the second speed driven gear 62 is rotated by the second input shaft 22, the reverse gear 70 is also rotated simultaneously.

  The second countershaft 32 is rotatably supported with respect to the transmission case 11 and the clutch housing 12 by a bearing, and is disposed in parallel to the first input shaft 21 in the transmission case 11. A final reduction drive gear 68 is formed on the outer peripheral surface of the second countershaft 32, and a portion for supporting the bearing and a plurality of external splines are formed. The clutch hubs 201 of the second and fourth shift clutches 102 and 104 are press-fitted into the external splines of the second countershaft 32 by spline fitting. Shift devices 110 that drive the second and fourth shift clutches 102 and 104 are provided on the peripheral wall above the transmission case 11 near the second and fourth shift clutches 102 and 104, respectively (see FIG. 2). Only the shift device 110 that drives the second shift clutch 102 is shown). The final reduction drive gear 68 meshes with a differential ring gear 80. Further, the second countershaft 32 is formed with a support portion that supports the second speed driven gear 62, the fifth speed driven gear 65, the sixth speed driven gear 66, and the seventh speed driven gear 67 so as to be freely rotatable.

  The second speed driven gear 62 is always meshed with a second speed drive gear 52 formed on the second input shaft 22. The 5-speed driven gear 65 is always meshed with a 5-speed drive gear 55 formed on the first input shaft 21. The sixth speed driven gear 66 is always meshed with a sixth speed drive gear 56 formed on the second input shaft 22. Further, the seventh-speed driven gear 67 is always meshed with a seventh-speed drive gear 57 that is supported by the second countershaft 32 so as to be free to rotate.

  As shown in FIG. 3, the dual clutch 40 includes a first clutch 41 that transmits the rotational driving force of the internal combustion engine E / G to the first input shaft 21, and the driving force of the internal combustion engine E / G that is supplied to the second input shaft 22. And a second clutch 42 for transmitting to The dual clutch 40 is accommodated in the clutch housing 12 on the right side of FIG. 1 and is provided concentrically with the first input shaft 21 and the second input shaft 22. The first clutch 41 is connected to the connecting portion of the first input shaft 21, and the second clutch 42 is connected to the connecting portion of the second input shaft 22. Then, the first and second clutches 41 and 42 are sequentially operated with respect to the first and second input shafts 21 and 22 on the basis of the vehicle control command to switch the connection with the internal combustion engine E / G, thereby shifting at high speed. Changes are possible.

  As shown in FIG. 3, the ring gear 80 is meshed with the final reduction drive gear 58 and the final reduction drive gear 68, so that the ring gear 80 is always rotationally connected to the first auxiliary shaft 31 and the second auxiliary shaft 32. The ring gear 80 is connected to a drive wheel (not shown) of the vehicle via an output shaft 80a supported by the case 10 and a differential mechanism (not shown).

  Next, the first to fourth shift clutches 101 to 104 will be described. As shown in FIG. 3, the first shift clutch 101 is arranged between the first speed driven gear 61 and the third speed driven gear 63 in the axial direction of the first countershaft 31. The second shift clutch 102 is disposed between the second speed driven gear 62 and the sixth speed driven gear 66 in the axial direction of the second countershaft 32. The third shift clutch 103 is disposed between the fourth speed driven gear 64 and the reverse gear 70 in the axial direction of the first countershaft 31. Further, the fourth shift clutch 104 is disposed between the fifth speed driven gear 65 and the seventh speed driven gear 67 in the axial direction of the second countershaft 32.

  The first shift clutch 101 is press-fitted and fixed to a clutch hub 201 splined to the first countershaft 31, a first-speed engagement member 205 press-fitted to the first-speed driven gear 61, and a third-speed driven gear 63. A three-speed engagement member 205, a synchronizer ring 203 interposed between the clutch hub 201 and the left and right engagement members 205, 205, and a sleeve that is spline-engaged on the outer periphery of the clutch hub 201 so as to be axially movable. 202, and is a well-known synchromesh mechanism that removably connects the driven gears 61 and 63 to the first countershaft 31.

  The sleeve 202 of the first shift clutch 101 is not engaged with any of the engagement members 205 and 205 in the neutral position. However, the fork shaft 95 is driven in the input shaft direction by the operation of the shift device 110, and the sleeve 202 is moved to the first speed driven gear 61 side by the shift fork 91 engaged with the annular groove on the outer periphery of the sleeve 202 fixed to the fork shaft 95. Is shifted to the synchronizer ring 203 on the first speed driven gear 61 side by spline engagement. Then, the rotations of the first countershaft 31 and the first speed driven gear 61 are synchronized. Next, the sleeve 202 engages with an external spline on the outer periphery of the first-speed engagement member 205, and the first countershaft 31 and the first-speed driven gear 61 are integrally connected to form the first-speed stage. Further, if the shift fork 91 shifts the sleeve 202 toward the third speed driven gear 63 by the shift device 110, the rotation of the first countershaft 31 and the third speed driven gear 63 is similarly synchronized, and then the two are integrated. To form a third gear.

  The second to fourth shift clutches 102 to 104 are substantially the same in structure as the first shift clutch 101 and only have different attachment positions. The second shift clutch 102 selectively connects the second speed driven gear 62 and the sixth speed driven gear 66 to the second countershaft 32 to form the second speed and the sixth speed, and the third shift clutch 103 is the fourth speed driven. The gear 64 and the reverse gear 70 are selectively connected to the first countershaft 31 to form a fourth speed and a reverse speed, and the fourth shift clutch 104 connects the fifth speed driven gear 65 and the seventh speed driven gear 67 to the first auxiliary gear 31. A fifth gear and a seventh gear are formed by selectively connecting to the shaft 31.

  Next, each shift device 110 according to the present invention for driving the first to fourth shift clutches 101 to 104 will be described with reference to FIGS. 2 and 4 to 6. Each shift device 110 is fixed to the upper peripheral wall of the transmission case 11 by bolts (not shown). Each shift device 110 is detachably attached to the peripheral wall of the transmission case 11.

  As shown in FIGS. 4 to 6, the shift device 110 includes a case 111, a motor 114, a pinion shaft 116, a reduction gear mechanism 118, a support plate 120, a fixing portion 122, a rotation regulating portion 124, A fork shaft 95 and a shift fork 91 are provided.

  The case 111 has a bottom wall 113 formed by a part of the peripheral wall of the upper case 112 and the transmission case. The upper case 112 is an aluminum member manufactured by die casting or casting, for example. However, the manufacturing method and material are not limited to this, and any method may be used. For example, it may be manufactured by processing or forging, and brass or iron-based material may be used as the material. As shown in FIGS. 4 and 5, the upper case 112 has a ceiling wall 112b having an L shape in a top view, and the first to sixth side walls 131 to 136 extend from each side of the ceiling wall 112b. In the state of being attached to the peripheral wall, the wall is erected downward in the direction of gravity. The first side wall 131 faces the third side wall 133 and the fifth side wall 135, and the second side wall 132 faces the fourth side wall 134 and the sixth side wall 136. And the lower end side of the 1st thru | or 6th side walls 131-136 facing the ceiling wall 112b is opened without having a wall.

  From the lower ends of the first to sixth side walls 131 to 136, a flange portion 112a is erected with a predetermined width toward the outside of the upper case 112, and an opening peripheral edge portion 112d is formed on the lower surface of the flange portion 112a. A plurality of through holes (not shown) for inserting bolts are formed in the flange portion 112a.

  An opening peripheral edge portion 112d of the flange portion 112a is attached to an attachment portion 113a of a bottom wall 113 formed in the transmission case 11, and is fixed to the transmission case 11 by a bolt (not shown) inserted through a through hole. By fixing the upper case 112 to the bottom wall 113 in this way, a case 111 having a gear chamber 111a for holding the reduction gear mechanism 118 is formed.

  The fixing portion 122 is formed integrally with the upper case 112 and is erected downward from the ceiling wall 112b of the upper case 112 along the fourth side wall 134 into the gear chamber 111a. The fixing part 122 has a support surface 123 to which the upper surface of the support plate 120 is screwed, and the support plate 120 is screwed to the support surface 123 of the fixing part 122 by bolts 140. At this time, a screwing portion is formed by the internal thread formed on the bolt 140 and the fixing portion 122. The position of the support surface 123 of the fixing portion 122 in the axial direction of the bolt 140 is such that when the upper case 112 is attached to the bottom wall 113 of the transmission case 11, a predetermined distance D1 is formed with respect to the upper surface of the attachment portion 113a of the bottom wall 113. That is, the flange 112a is formed such that the distance from the opening peripheral edge 112d is D1 (see FIG. 6). The predetermined distance D1 will be described in detail later.

  Further, as shown in FIGS. 5 and 6, a motor support portion 112 c that supports the motor 114 and is formed integrally with the upper case 112 is formed in the upper case 112. The motor support portion 112c is erected in the gear chamber 111a downward from the ceiling wall 112b of the upper case 112. The motor support portion 112c may be formed in any shape, but has a rectangular parallelepiped shape in the present embodiment. An attachment surface 137 is formed so that the output shaft 114a of the motor 114 is parallel to the flat portion of the first side wall 131 and the ceiling wall 112b, and the flange portion 114b of the motor 114 is fixed to the attachment surface 137. The motor support portion 112c is provided with an output shaft through hole 138 so that the output shaft 114a passes through when the motor 114 is attached.

  On the side surface 139 on the third to fifth side walls 133, 134, 135 side of the motor support portion 112c, a rotation restricting portion 124 that comes into contact with a P portion of the support plate 120 described later is provided. The rotation restricting portion 124 is for restricting the rotation of the support plate 120 with the center of the screwed portion of the support plate 120 screwed to the fixing portion 122, that is, the shaft center of the bolt 140 as the rotation axis. When the support plate 120 is screwed to the fixing portion 122, a predetermined gap is formed between the inner diameter of a through hole (not shown) of the support plate 120 and the outer diameter of the bolt 140 that passes through the through hole. Has been. That is, before fixing the support plate 120 with the bolts 140, the P portion that is the contact portion of the support plate 120 is moved toward the rotation restricting portion 124 side of the motor support portion 112c using a predetermined gap. Then, the support plate 120 is fixed by tightening the bolt 140 with the rotation restricting portion 124 and the P portion in contact with each other. Thus, the optimum size of the inner diameter of the through hole is acquired and determined by prior examination so that the support plate 120 can be fixed. Thereby, the rotation of the support plate 120 can be well regulated.

  The bottom wall 113 is formed on a part of the peripheral wall of the transmission case 11. The bottom wall 113 has a recess 113b that is recessed with respect to the peripheral wall of the transmission case 11 forming the gear chamber 111a, and the peripheral edge of the recess 113b has substantially the same height as the peripheral wall of the transmission case 11, and the opening peripheral edge of the upper case 112 It has the attachment part 113a which contact | abuts the part 112d.

  A cylindrical wall 141 (corresponding to the annular support portion of the present invention) is provided in the recess 111 b of the bottom wall 113 so as to protrude in the case 111 coaxially with the pinion shaft 116. An oil seal 142 as a seal member is interposed between the pinion shaft 116 and the cylindrical wall 141 in a liquid-tight manner (see FIG. 4). This prevents oil in the transmission case 11 from leaking to the outside, and prevents water, dust, and dust from entering the transmission case 11 through the case 111. A through hole 143 is formed in the bottom surface of the cylindrical wall 141 coaxially with the pinion shaft 116, and a cylindrical bearing 148 is press-fitted into the inner peripheral portion, and the pinion shaft 116 is inserted into the bearing 148. As a result, the bearing 148 supports one end of the pinion shaft 116.

  In addition, a bottomed bearing hole 146 for supporting a lower end portion of a worm wheel shaft 119 constituting a reduction gear mechanism 118 described later is formed in the recess 113b of the bottom wall 113. At this time, the bottom surface of the bearing hole 146 is formed to have a predetermined depth. The predetermined depth will be described later. A cylindrical bearing 149 is press-fitted into the inner periphery of the bearing hole 146, and the bearing 149 supports the lower end of the worm wheel shaft 119.

  The motor 114 is connected to a control device (not shown), and the rotation angle of the output shaft 114a is controlled by a command signal sent from the control device. Any motor 114 may be used. However, in the present embodiment, a stepper motor that rotates in response to pulse power that can be accurately angle-controlled is applied. However, the present invention is not limited to this, and any motor may be used as long as the rotation speed (rotation angle) can be controlled. A worm 144 constituting a reduction gear mechanism 118 that is rotationally driven by the motor 114 is formed at the tip of the output shaft 114 a of the motor 114. As described above, the motor 114 is fixed to the mounting surface 137 of the motor support portion 112c by fixing the flange portion 114b with a bolt (not shown), and the coil portion of the motor 114 has first, fifth side walls 131, 135 and It is held between the ceiling walls 112b.

  As described above, as shown in FIG. 4, the pinion shaft 116 is a ceiling in the state where the upper case 112 in which the motor 114, the pinion shaft 116 and the reduction gear mechanism 118 are assembled is attached to the bottom wall 113 of the transmission case 11. Both ends are detachably supported by a bearing 145 on the wall 112b and an oil seal 142 and a bearing 148 press-fitted into the through hole 143 disposed in a cylindrical wall 141 provided in the recess 113b. The pinion shaft 116 protrudes a predetermined amount into the transmission case 11, and a pinion 116a is formed at the protruding end.

  The reduction gear mechanism 118 is a reduction mechanism that reduces the speed from the worm 144 formed on the output shaft 114a of the motor 114 to the pinion shaft 116 in two stages. Specifically, as shown in FIGS. 4 to 6, the reduction gear mechanism 118 includes a worm 144, a worm wheel 119a, a small diameter reduction gear 119b, and a large diameter reduction gear 116b. The worm 144 meshes with a worm wheel 119a (corresponding to a reduction gear of the present invention) fixed coaxially to the worm wheel shaft 119. A small diameter reduction gear 119b (a spur gear corresponding to the reduction gear of the present invention) having a smaller diameter than the worm wheel 119a is fixed coaxially with the worm wheel 119a below the worm wheel 119a in the axial direction of the worm wheel shaft 119. ing. The worm wheel shaft 119 is supported by a bearing 147 provided in the ceiling wall 112b and a bearing 149 press-fitted into a bearing hole 146 formed in the recess 113b of the bottom wall 113. A large-diameter reduction gear 116b (a spur gear corresponding to the reduction gear of the present invention) is fixed to the pinion shaft 116 coaxially with the pinion shaft 116 and meshes with the small-diameter reduction gear 119b. With such a configuration, when the motor 114 rotates, the rotation of the pinion shaft 116 is reduced through the reduction gear mechanism 118 and is driven to rotate.

  The support plate 120 is a flat member formed of a ferrous metal plate member such as SPCC or SPCE. In FIG. 5, the support plate 120 has a shape in which the T-shape is horizontal. The support plate 120 is provided with the above-described through hole (not shown) for inserting the bolt 140 at the lower end in FIG. As described above, the inner diameter of the through hole is formed to be larger by a predetermined amount than the shaft diameter of the bolt 140 to be inserted.

  Here, the relationship between the P portion and the rotation restricting portion 124 will be briefly described. The support plate 120 is screwed at one point by a bolt 140 to a fixing portion 122 constituting a screwing portion. For this reason, when an external force is applied to the support plate 120, the support plate 120 may be rotated about the axis of the bolt 140. For this reason, the rotation restricting portion 124 that contacts the P portion is required not to allow the support plate 120 to rotate in any direction. Therefore, in the present invention, a perpendicular is drawn from the axial center of the bolt 140 to the side surface 139 of the motor support portion 112c, and the rotation restricting portion 124 is set so as to contact the P portion on the upper side and the lower side in FIG. As a result, the support plate 120 can not rotate in any direction around the axis of the bolt 140 and can be well controlled in rotation.

  Further, the lower surfaces of the small-diameter reduction gear 119b and the large-diameter reduction gear 116b are supported from below in the gravitational direction at predetermined positions by the upper surfaces of the other portions of the support plate 120. At this time, the predetermined position means that when the upper case 112 to which the motor 114, the pinion shaft 116, and the reduction gear mechanism 118 are assembled is fixed to the mounting portion 113a of the bottom wall 113 of the transmission case 11, the small diameter reduction gear 119b and the large diameter reduction gear 119b. It means a position where the flat portion of the radial reduction gear 116b is appropriately separated from the support plate 120 that has been supported so far. At this time, the separation size may be a size that can be managed by a standard design.

  Specifically, the large-diameter reduction gear 116b fixed to the pinion shaft 116 is lowered by the support plate 120 during the lowering when the opening peripheral edge 112d of the upper case 112 is lowered and fixed toward the mounting portion 113a. The lower surface of the large-diameter reduction gear 116 b that supports the cylinder is in contact with the upper surface of the cylindrical wall 143 provided on the bottom wall 113. As a result, movement of the pinion shaft 116 to which the large-diameter reduction gear 116b is fixed in the axial direction is restricted in the middle, and only the support plate 120 is lowered together with the upper case 112, and the support plate 120 eventually becomes a plane of the large-diameter reduction gear 116b. Separated from the part. As described above, when the upper case 112 is fixed to the mounting portion 113a, the position of the upper surface of the support plate 120 for the support plate 120 to be separated from the plane portion of the large-diameter reduction gear 116b, that is, the fixing to which the support plate 120 is fixed. The position of the support surface 123 of the portion 122 is referred to as a predetermined position.

  Further, with respect to the small-diameter reduction gear 119b fixed to the worm wheel shaft 119, when the opening peripheral edge portion 112d of the upper case 112 is lowered and fixed toward the mounting portion 113a, the lower end of the worm wheel shaft 119 is bottomed during the lowering. It abuts against the bottom surface of the bearing hole 146 provided in the wall 113. As a result, the movement of the worm wheel shaft 119 and the small diameter reduction gear 119b in the axial direction is restricted in the middle, and only the support plate 120 is lowered together with the upper case 112, and the support plate 120 is separated from the plane portion of the small diameter reduction gear 119b. As described above, when the upper case 112 is fixed to the attachment portion 113a, the position of the upper surface of the support plate 120 for the support plate 120 to be separated from the flat portion of the small diameter reduction gear 119b, that is, the fixing portion to which the support plate 120 is fixed. The position of the support surface 123 of 122 is called a predetermined position. At this time, the predetermined position is defined by the distance from the opening peripheral portion 112d of the flange portion 112a in the axial direction of the pinion shaft 116 as described above (see D1 in FIG. 6). As a result, when the shift device 110 is operated, the support plate 120, the small diameter reduction gear 119b, and the large diameter reduction gear 116b are reliably separated from each other and do not come into contact with each other. Can operate.

  In the first embodiment, the rotation restricting portion 124 is provided on the motor support portion 112c. However, the present invention is not limited to this, and a part of the support plate is formed as shown by a two-dot chain line in FIG. It is good also as a rotation control part. Two types of two-dot chain lines are shown, and either one may be applied. Further, two or more rotation restricting portions may be provided and simultaneously contacted with the support plate 120 at two or more locations.

  In the first embodiment, the fixing portion 122 is provided at the position shown in FIG. 5. However, the present invention is not limited to this, and the fixing plate 122 may be provided anywhere as long as the support plate 120 can be fixed under the conditions described above.

  As is clear from the above description, according to the first embodiment, the shift device 110 does not have a selection mechanism, and the fork shaft 95 is operated in the axial direction only by the rotational operation of the pinion shaft 116, and the gear position is switched. To do. When the shift device 110 is attached to the peripheral wall of the transmission case 11, the worm wheel shaft 119 (including the worm wheel 119 a and the small-diameter reduction gear 119) constituting the reduction gear mechanism 118 from the opening directed downward in the gravitational direction. A support plate 120 is provided so that the pinion shaft 116 (including the large-diameter reduction gear 116b) does not fall. The support plate 120 is screwed and fixed to the fixing portion 122 in the upper case 112, and is also in contact with the rotation restricting portion 124 provided in the upper case 112 to restrict the rotation about the screwed portion center as the rotation axis. At this time, since the shift device 110 does not have a selection mechanism, the reduction gear mechanism 118 has a simple configuration, and the support plate 120 can be reduced in size and weight. Thereby, the rotation restricting portion 124 can be simply formed, and a low-cost and lightweight shift device can be realized.

  In addition, according to the first embodiment, the rotation restricting portion 124 is provided on at least one of the motor support portion 112c and the inner peripheral wall of the upper case 112 in the upper case 112, so it is necessary to change the shape in the case. A low-cost and lightweight shift device can be realized.

  Further, according to the first embodiment, when the upper case 112 is attached to the bottom wall 113 (circumferential wall) of the transmission case 11, the lower surface of the large-diameter reduction gear 116 b (reduction gear) is provided on the bottom wall 113. It is separated from the support plate 120 by being supported on the upper surface of the cylindrical wall 141 (annular support). Accordingly, when the shift device 110 is operated, the large-diameter reduction gear 116b can be operated satisfactorily without receiving the rotational resistance by the support plate 120.

  Next, a shift device 150 according to the second embodiment will be described with reference to FIGS. The shift device 150 of the second embodiment is provided with two motors 114, two pinion shafts 116, and two reduction gear mechanisms 118 in one case 151, respectively, with respect to the shift device 110 of the first embodiment. Only the point is different. Thus, only different points will be described, and description of similar points will be omitted. The same parts are described with the same reference numerals.

  As shown in FIGS. 7 and 8, the shift device 150 includes a case 151, two motors 114, two pinion shafts 116, two reduction gear mechanisms 118, a support plate 160, a fixing portion 162, A rotation restricting portion 164, a fork shaft 95, and a shift fork 91 are provided (see FIG. 2 for the fork shaft 95 and the shift fork 91).

The case 151 has a bottom wall 153 formed by a part of the peripheral wall of the upper case 152 and the transmission case. As shown in FIGS. 7 and 8, the upper case 152 has a ceiling wall 152b having a rectangular top view, and the first to fourth side walls 171 to 174 are peripheral walls of the transmission case 11 from each side of the ceiling wall 152b. In the attached state, it is erected downward in the direction of gravity. And the lower end side of the 1st thru | or 4th side walls 171-174 which oppose the ceiling wall 152b is opened without a wall.
From the lower ends of the first to fourth side walls 171 to 174, a flange 152a is erected with a predetermined width toward the outside of the upper case 152, and an opening peripheral edge 152d is formed on the lower surface of the flange 152a. A plurality of through holes (not shown) for inserting bolts are formed in the flange portion 152a.

  An opening peripheral portion 152d of the flange portion 152a is attached to an attachment portion 153a of a bottom wall 153 formed in the transmission case 11, and is fixed to the transmission case 11 by a bolt (not shown) inserted through a through hole. By fixing the upper case 152 to the bottom wall 153 in this way, a case 151 having a gear chamber 151a for holding the two reduction gear mechanisms 118 is formed.

  The fixing portion 162 is formed integrally with the upper case 152 and is erected downward from the ceiling wall 152b of the upper case 152 into the gear chamber 151a. The fixed portion 162 has a support surface 161 to which the upper surface of the support plate 160 is screwed, and the upper surface of the support plate 160 is screwed to the support surface 161 of the fixed portion 162 with a bolt 180. The position of the support surface 161 of the fixing part 162 in the axial direction of the bolt 180 is formed such that when the upper case 152 is attached to the bottom wall 153 of the transmission case 11, the distance from the opening peripheral part 152d of the flange part 152a becomes D2. (See FIG. 8). The predetermined distance D2 is the same as D1 in the first embodiment.

Further, as shown in FIGS. 7 and 8, two motor support portions 152 c that support the motor 114 and are formed integrally with the upper case 152 are formed in the upper case 152. The two motors 114 and the motor support part 152c are arranged in a state of being rotated about 180 degrees around the bolt 180 axis of the fixed part 162. A rotation restricting portion 163 for restricting the rotation of the support plate 160 is provided on each of the side surfaces 179 facing the two motor support portions 152c.
Further, in the upper case 152, two pinion shafts 116 and two reduction gear mechanisms 118 each having the same configuration and operation as the shift device 110 of the first embodiment are provided.

  The bottom wall 153 has the same structure as the bottom wall 113 of the first embodiment. Two cylindrical walls 181 (corresponding to the annular support portion of the present invention) are provided in the recess 151 153 of the bottom wall 153 so as to be coaxial with the pinion shaft 116 and project in the case 151 coaxially with the pinion shaft 116. .

  Also, in the recess 153 b of the bottom wall 153, two bottomed bearing holes 186 that support the lower end portion of the worm wheel shaft 119 constituting the reduction gear mechanism 118 are formed coaxially with each worm wheel shaft 119. A cylindrical bearing is press-fitted. At this time, the bottom surface depth of each bearing hole 186 is formed to be the predetermined depth described in the first embodiment.

  The support plate 160 is formed in the planar shape shown in FIG. A P portion (contact portion) is formed at a portion of the support plate 160 that contacts the rotation restricting portion 163 of the motor support portion 152c. In addition, the P part should just contact | abut either of the rotation control parts 163 of the two motor support parts 152c.

  A through hole (not shown) through which the bolt 180 is inserted is provided at the substantially center of gravity of the support plate 160. As in the first embodiment, the inner diameter of the through hole is slightly larger than the shaft diameter of the bolt 180 to be inserted. As a result, when the bolt 180 is inserted into the through hole of the support plate 160, the support plate 160 is moved by the gap between the outer diameter of the bolt 180 and the inner diameter of the through hole. ) Can be properly brought into contact with the rotation restricting portion 163 of the motor support portion 152c.

  Further, the upper surface of the support plate 160 is configured so that the planar portions of the two small diameter reduction gears 119b and the two large diameter reduction gears 116b are supported from below in the gravitational direction at the predetermined positions described in the first embodiment. . Thus, when the upper case 152 is fixed to the mounting portion 153a of the bottom wall 153, the support plate 160 is connected to each large diameter reduction gear 116b with respect to the two large diameter reduction gears 116b fixed to each pinion shaft 116. The pinion shafts 116 do not fall from the openings. Further, during the lowering of the upper case 152, the lowering of each pinion shaft 116 is restricted by the lower surface of the large-diameter reduction gear 116 b coming into contact with the upper surface of the cylindrical wall 181. For this reason, only the support plate 160 is lowered together with the upper case 152 and is separated from the plane portions (lower surfaces) of the two large-diameter reduction gears 116 b fixed to the pinion shafts 116.

  For each small diameter reduction gear 119b fixed to each worm wheel shaft 119, when the upper case 152 is fixed to the mounting portion 153a of the bottom wall 153, the small diameter reduction gear 119b is supported by the support plate 160, so Does not fall. In the middle of lowering of the upper case 152, when the lower end of the worm wheel shaft 119 comes into contact with the bottom surface of the bearing hole 186 provided in the bottom wall 153, the worm wheel shaft 119 and the small diameter reduction gear 119b move in the axial direction. Is regulated on the way. For this reason, only the support plate 120 is lowered together with the upper case 152 and separated from the flat surface portion (lower surface) of the small diameter reduction gear 119b.

  As a result, the support plate 160 is not in contact with the two small diameter reduction gears 119b and the two large diameter reduction gears 116b when the shift device 150 is operated, so that each small diameter reduction gear 119b and the large diameter reduction gear 116b are good without causing resistance. Can be operated. In addition, the support plate 160 is screwed and fixed to the fixing portion 162 in the upper case 152, and is abutted against the rotation restricting portion 163 of the upper case 152 to restrict the rotation about the screwed portion center as the rotation axis. The Thus, even after the shift device 150 is attached to the peripheral wall of the transmission case 11, there is no possibility that the support plate 160 is rotated by the vibration of the motor 114, the bolt 180 is loosened, and the bolt 180 and the support plate 160 are dropped.

  In addition, in 2nd Embodiment, although the fixing | fixed part 122 was provided in the position shown in FIG. 7, not only this but the support plate 160 may be arrange | positioned anywhere if it can fix on the conditions described above. .

  In the first and second embodiments, the reduction gear mechanism 118 is configured to decelerate in two stages by the reduction gears of the worm wheel shaft 119 and the pinion shaft 116, respectively. However, the worm wheel 119a is fixed coaxially to the pinion shaft 116, and the worm 144 formed on the output shaft 114a of the motor 114 and the worm wheel 119a of the pinion shaft 116 are not limited to such a mode of decelerating in two stages. It is good also as a 1-stage reduction mechanism directly meshing. Furthermore, the reduction gear mechanism 118 may be a reduction mechanism having three or more stages. The same effect can be obtained by these.

  In the first and second embodiments, the dual clutch automatic transmission having the seventh forward speed is described as the dual clutch automatic transmission according to the present invention. However, the present invention is not limited to this mode, and the dual clutch automatic transmission may have a forward shift speed exceeding 7th speed or a forward shift speed not exceeding 6th speed. This also provides the same effect.

  In the first and second embodiments, the invention is embodied by the dual clutch type automatic transmission. However, the invention is not limited to this, and the invention is applied to an automated manual transmission (AMT) in which the clutch of the manual transmission is automated. May be.

  Furthermore, the shift devices 110 and 150 may be applied to other automatic transmissions such as motorcycles instead of being applied to automatic transmissions for automobiles.

DESCRIPTION OF SYMBOLS 1 ... Automatic transmission, 10 ... Case, 11 ... Transmission case, 12 ... Clutch housing, 91 ... Shift fork, 95 ... Fork shaft, 110, 150 ... Shift device 112, 152 ... upper case, 113, 153 ... bottom wall, 114 ... motor, 116 ... pinion shaft, 118 ... gear reduction mechanism, 119 ... worm wheel shaft, 120, 160 ... support plate, 122,162 ... fixed portion, 124,163 ... rotation restricting portion.

Claims (3)

A case in which a part of the peripheral wall of the transmission case is a bottom wall and an upper case is fixed to the bottom wall at the periphery of the opening, and a gear chamber is formed inside;
A motor supported in the case;
Both ends of the upper case are removably supported on the ceiling wall and the bottom wall, and a pinion shaft on which the pinion is formed; and
A reduction gear mechanism having a reduction gear interposed between the output shaft of the motor and the pinion shaft and fixed to the pinion shaft;
When the upper case assembled with the motor, the pinion shaft, and the reduction gear mechanism is attached to the peripheral wall of the transmission case, the reduction gear and the gear meshing with the reduction gear do not fall from the opening of the upper case. A support plate for supporting the lower surface of the gear that meshes with the reduction gear and the reduction gear from below in the direction of gravity;
A fixing portion formed in a predetermined position with respect to a lower surface of the opening peripheral portion, a support surface provided in the upper case and screwed to the support plate;
A rotation restricting portion that is provided in the upper case, contacts the support plate, and restricts the rotation of the support plate around the center of a screwed portion that screws the support plate to the fixed portion;
A fork shaft having a rack meshing with the pinion and supported in an axially movable manner in the transmission case;
A shift device for an automatic transmission, comprising: a shift fork fixed to the fork shaft.   2. The shift device for an automatic transmission according to claim 1, wherein the rotation restricting portion is provided on at least one of a support portion of the motor and an inner peripheral wall of the upper case in the upper case. In claim 1 or 2,
In a state in which the upper case is attached to the peripheral wall of the transmission case, the reduction gear is supported by an annular support portion that is provided on the bottom wall and supports the pinion shaft, and is automatically separated from the support plate. Shift device for transmission.

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