JP2017053470A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission which facilitates assembling operation of a transmission, minimizes joint spots of casing and can suitably prevent distortion of a transmission casing upon high loading.SOLUTION: All shafts (an input shaft 13, a first output shaft 14, a second output shaft 15, a shaft of intermediate transmission idle gear 54B and a reverse idle shaft 17) excluding driving shafts 35, 35 are supported by an intermission plate 102. Further, alignment regulation regarding an axial direction between a first pulley 21 and a second pulley 22 is performed on the basis of the intermission plate 102 as a reference. Therein, the alignment regulation is performed by changing a plate thickness value t of an alignment regulation shim S assembled between a second stationary pulley 22A and a bearing BR2. Further, the intermission plate 102 is assembled on the inner side of a mission case 100 and the mission case 100 and a torque converter case 101 are assembled in a circumferential direction in an abutted form.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a shaft support structure for a continuously variable transmission having auxiliary transmission mechanisms before and after a pulley.

  As a bearing structure of a pulley shaft of a belt-type continuously variable transmission (pulley), a transmission case that houses the pulley is a first case (front case) positioned on the torque converter side and a second case positioned on the opposite side of the torque converter. The belt is configured to be divided into two parts by a case (rear case), and the pulley shaft is rotatably supported by a first bearing provided in the partition wall of the first case and a second bearing provided in the partition wall of the second case. 2. Description of the Related Art A pulley shaft bearing structure of a continuously variable transmission is known (see, for example, Patent Document 1).

JP 2010-53879 A

  In the pulley shaft bearing structure described in Patent Document 1, the input shaft of the torque converter is spline fitted to the inner peripheral surface of the drive pulley shaft, and the tip of the drive pulley shaft is provided by the first bearing provided in the first case. It is rotatably supported. That is, the entire drive system shaft is supported by the first case via the first bearing.

  Further, for example, a rear end portion of the drive pulley shaft on the rear side cover side is provided with a shim for position adjustment, and the rear end portion of the drive pulley shaft is used as a reference (of the movable pulley) by changing the thickness of the shim. The axial position of the cylinder member is adjusted. After the axial position of the cylinder member is adjusted (determined), the shim, the cylinder member, and the second bearing are positioned on the rear end portion of the drive pulley shaft by tightening the self-lock nut (see Patent Document 1). [0054].

  That is, in the pulley shaft bearing structure described in Patent Document 1, when assembling the transmission, components are assembled to the input shaft and the pulley shaft in order from the torque converter side to the pulley side, and the pulley is installed at the rear end of the pulley shaft. The position in the axial direction is adjusted.

  However, when parts are assembled to the shaft in order from the torque converter side to the pulley side, the number of dimensional tolerances of the parts will increase, resulting in complicated adjustment of the axial position of the pulley, resulting in shifting There arises a problem that the assembly work of the machine becomes complicated.

  In addition, since the first case is joined to the second case at one end and joined to the torque converter case at the other end, the joining hierarchy from the second case to the torque converter case is increased and the number of joints of the case is increased. In addition, problems such as distortion (decrease in rigidity) of the case at high load occur.

  SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems of the prior art. The purpose of the present invention is to facilitate the assembly work of the transmission, and to shift gears at high loads while minimizing the joints of the case. An object of the present invention is to provide a shaft support structure for a continuously variable transmission that can suitably prevent distortion of a machine case.

In the continuously variable transmission according to the present invention for achieving the above object, the driving force from the engine output shaft (11) input to the input shaft (13) is transmitted via the gear mechanism (51, 52) to the driving pulley ( 21 and 22), and a driving force transmitting member (23) wound between the driven pulley (22, 21) and the driving pulley (21, 22) paired with the driving pulley (21, 22). ) Through which the driving force is transmitted to the driven pulleys (22, 21),
A transmission case (100) which accommodates the drive pulleys (21, 22) and the driven pulleys (22, 21) and rotatably supports one side of each rotation shaft (14A, 15A) of each pulley in the axial direction. )When,
A power transmission mechanism case (101) that houses a power transmission mechanism (12) that transmits the driving force from the engine output shaft (11) to the input shaft (13);
The other side of the rotating shafts (14A, 15A) of the driving pulleys (21, 22) and the driven pulleys (21, 22) are supported rotatably or directly and the input shaft (13) is rotated. An intermediate plate (102) that supports it,
The intermediate plate (102) is assembled to the inside of the transmission case (100), and the transmission case (100) is assembled to the power transmission mechanism case (101) in a state where the axial end surfaces thereof are abutted with each other. It is characterized by being able to.

  In the above configuration, the intermediate plate (102) is coupled only to the transmission case (100). Further, the rotating shafts (14A, 15A) and the input shaft (13) of the driving pulley and the driven pulley are rotatably supported by the intermediate plate (102) directly or indirectly. Therefore, the intermediate plate (102) can be used as a positioning reference for positioning (alignment adjustment) of the pulleys (21, 22). When each pulley (21, 22) is positioned with respect to the intermediate plate (102), the component located on one side of the intermediate plate (102) and the component located on the other opposite side are shifted. It becomes possible to assemble along the respective axes separately and independently while reversing the assembly state of the machine. As a result, the transmission can be easily assembled. In addition, since alignment adjustment at the end of the pulley (21, 22) on the transmission case (100) side is not necessary, it is not necessary to provide a side cover for alignment adjustment on the transmission case (100).

  Further, since the transmission case (100) is joined only to the power transmission mechanism case (101), it is possible to minimize the joints of the transmission case (100).

  Further, the transmission case (100) is formed as a single piece (one piece), and the power transmission mechanism case (101) is abutted and joined to the open end (C1) thereof. Further, the transmission case (100) is coupled to the intermediate plate (102) inside. As a result, the rigidity of the transmission case (100) is improved by assembling the power transmission mechanism case (101) and the intermediate plate (102) to the transmission case (100), and the transmission case (100) at the time of high load. It becomes possible to prevent distortion.

  A second feature of the transmission mechanism according to the present invention is that the transmission (1) includes a synchronous engagement device (71, 72, 73), and a shift actuator that drives a sleeve (71) of the synchronous engagement device. (74) is disposed on the surface of the intermediate plate (102).

  In the above configuration, the intermediate plate (102) serves as a positioning reference for assembling the forward / reverse switching mechanism (70). When the intermediate plate (102) serves as a positioning reference, both the abutting position of the sleeve (71) of the synchronous engagement device and the position of the piston (74a) of the hydraulic shift actuator (74) are both based on the intermediate plate (102). To be positioned. Therefore, the number of tightly stacked parts is reduced, resulting in less backlash between the parts, and the forward / reverse switching mechanism (70) can be assembled to the intermediate plate (102) with high accuracy.

  A third feature of the speed change mechanism according to the present invention is that at least a portion of the driving force transmission member (23) in the circumferential direction is at least within the range of the axial width of the driving pulley or the driven pulley. The cover member (103) covering (23) is disposed on the intermediate plate (102).

  In the above configuration, a large amount of oil used for lubricating the driving force transmission member can be directly returned to the oil pan by the cover member. As a result, it is possible to prevent a part of the power transmitted to the rotation mechanism such as a gear from being consumed as power related to oil agitation.

  A fourth feature of the speed change mechanism according to the present invention is that the drive pulley and the driven pulley are disposed between the drive pulley (21, 22) or the driven pulley (21, 22) and the intermediate plate (102). An alignment adjusting member (S) for adjusting the alignment in the axial direction is provided.

  In the above configuration, the alignment adjustment in the axial direction between both pulleys is completed in the step of assembling the intermediate plate (102) to the drive pulley and the driven pulley. As a result, the assembly of the transmission is facilitated, and alignment adjustment at the shaft end portion of the drive pulley or the driven pulley is not necessary.

  According to the continuously variable transmission of the present invention, the assembly work of the transmission is facilitated, and distortion of the transmission case at a high load can be suitably prevented while minimizing the joint portion of the case. Become.

It is a skeleton figure showing a continuously variable transmission concerning one embodiment of the present invention. It is principal part sectional drawing which shows the assembly process of a 1st pulley. It is principal part sectional drawing which shows the assembly process of a 2nd pulley. It is principal part cross-sectional explanatory drawing which shows the assembly | attachment process of a 1st pulley and a 2nd pulley. It is principal part cross-sectional explanatory drawing which shows the assembly | attachment process of the intermediate plate with respect to a belt-type continuously variable transmission. It is explanatory drawing which shows the alignment adjustment of the axial direction between a 1st pulley and a 2nd pulley. It is principal part sectional drawing which shows the assembly | attachment process of the clutch drum of a 3rd friction clutch. It is principal part cross-sectional explanatory drawing which shows the assembly process of a subinput shaft and the last drive shaft. It is principal part cross-section explanatory drawing which shows the assembly | attachment process of the intermediate plate with respect to a sub input shaft and the last drive shaft. It is principal part cross-sectional explanatory drawing which shows the assembly | attachment process of a belt cover. It is a perspective view which shows the belt cover which concerns on this embodiment. It is principal part cross-sectional explanatory drawing which shows the assembly | attachment process of a forward / reverse switching mechanism. It is principal part sectional explanatory drawing which shows the assembly | attachment process of a mission case. It is principal part cross-sectional explanatory drawing which shows the inversion process of a transmission assembly. It is principal part cross-sectional explanatory drawing which shows the assembly | attachment process of a main input shaft and a 2nd drive shaft. It is principal part cross-sectional explanatory drawing which shows the assembly | attachment process of an intermediate transmission idle gear.

  Hereinafter, the present invention will be described in more detail with reference to embodiments shown in the drawings.

  FIG. 1 is a skeleton diagram of a continuously variable transmission 1 according to an embodiment of the present invention.

  As shown in FIG. 1, the continuously variable transmission 1 includes an input shaft 13 to which driving force is input from a driving source E via a torque converter 12, and a first output that is disposed in parallel to the input shaft 13. A so-called 1-input 2-output parallel triaxial structure having a shaft 14 and a second output shaft 15 is provided as a basic structure.

  The continuously variable transmission 1 includes a torque converter 12 as a power transmission mechanism that transmits the driving force from the drive source E to the transmission mechanism, and the first pulley 21, the second pulley 22, and the endless belt 23 as the main transmission mechanism. And a first transmission path 51, a second transmission path 52, a third transmission path 53, and an intermediate transmission path 54 before and after the belt-type continuously variable transmission 20 as an auxiliary transmission mechanism. And a first friction clutch 61, a second friction clutch 62, a third friction clutch 63, a fourth friction clutch 64, and a forward / reverse switching mechanism 70, respectively, as shift mode or transmission path selection mechanisms. Although not described in detail, the “shift mode” referred to here is an LO mode in which the first pulley 21 is a drive pulley and the output shaft is the second output shaft 15 and the pulley ratio is changed by a predetermined range. In addition, this refers to the HI mode in which the second pulley 22 is a driving pulley and the output shaft is the first output shaft 14 and the pulley ratio is changed by a predetermined range.

  In the continuously variable transmission 1, the entire transmission excluding the torque converter 12 is covered with a transmission case (transmission case) 100, and the torque converter 12 is covered with a torque converter case (power transmission mechanism case) 101. . The transmission case 100 and the torque converter case 101 are coupled along the circumferential direction in such a form that the opening end surfaces in the axial direction face each other at the joint portion C1 (not shown).

  Further, an intermediate plate (intermediate plate) 102 is attached to the inside of the mission case 100. All the shafts (input shaft 13, first output shaft 14, second output shaft 15, intermediate transmission idle gear 54B and reverse idle shaft 17) except the drive shafts 35, 35 of the final output mechanism 30 are connected to the intermediate plate 102. It is supported via bearings BR2, BR3, BR5, BR7.

  A belt cover 103 that covers the endless belt 23 is provided on the radially outer side of the endless belt 23 wound around the first pulley 21, and the belt cover 103 is fixed on the intermediate plate 102. Hereinafter, each configuration will be further described.

  The input shaft 13 includes a main input shaft 13A that is spline-coupled with the turbine runner 12A of the torque converter 12, and a sub input shaft 13C that has the same rotation center as the main input shaft 13A and is connected via a second friction clutch 62. Is done. The main input shaft 13A is concentrically and rotatably inserted into the sub input shaft 13C. A clutch drum 61a of the first friction clutch 61 is attached to the outer peripheral surface of the main input shaft 13A by spline coupling, and a clutch drum 62a of the second friction clutch 62 is installed inside the clutch drum 61a of the first friction clutch 61. Are attached by spline connection. On the other hand, the clutch hub 61b of the first friction clutch 61 is directly connected to a first transmission drive gear 51A described later, and the clutch hub 62b of the second friction clutch 62 is attached to the outer peripheral surface of the sub input shaft 13C by spline connection. Yes. Accordingly, when the first friction clutch 61 is engaged and the second friction clutch 62 is released, the main input shaft 13A is connected to the first transmission drive gear 51A while the first friction clutch 61 is released. At the same time, when the second friction clutch 62 is engaged, it is connected to the auxiliary input shaft 13C.

  The first output shaft 14 includes a first pulley shaft 14A that is a rotation shaft of the first pulley 21, and a final drive shaft 14B to which the final drive gear 31 and the intermediate transmission driven gear 54C are attached so as not to be relatively rotatable. The The final drive shaft 14B passes through the first pulley shaft 14A concentrically and rotatably. A clutch drum 64a of the fourth friction clutch 64 is attached to the outer peripheral surface of the final drive shaft 14B by spline coupling, and a third transmission driven gear 53C described later is provided on the outer peripheral surface of the clutch drum 64a in the radial direction. It is provided integrally. The clutch hub 64b of the fourth friction clutch 64 is integrally attached to the first fixed pulley 21A of the first pulley 21. Therefore, when the fourth friction clutch 64 is fastened, the first pulley shaft 14A and the final drive shaft 14B rotate together.

  The second output shaft 15 includes a second pulley shaft 15A that is a rotation shaft of the second pulley 22, and a second drive shaft 15B to which an intermediate transmission drive gear 54A is attached so as not to be relatively rotatable. The second drive shaft 15B is inserted concentrically and rotatably inside the second pulley shaft 15A. A clutch drum 63a of the third friction clutch 63 is attached by spline coupling to the outer peripheral surface of the shaft end portion of the second pulley shaft 15A on the back surface side of the second fixed pulley 22A. The clutch hub 63b that forms a pair with the clutch drum 63a is attached to the outer peripheral surface of the shaft end portion of the second drive shaft 15B by spline connection.

  The intermediate transmission idle gear 54B has an integrated gear and shaft, and the shaft is rotatably attached to the intermediate plate 102 and the torque converter case 101 via bearings BR7 and BR8.

  The reverse idle shaft 17 is fixed to the intermediate plate 102 so as not to rotate, and a third transmission idle gear 53B is rotatably attached thereto.

  A belt-type continuously variable transmission 20 is disposed between the first output shaft 14 (first pulley shaft 14A) and the second output shaft 15 (second pulley shaft 15A). The belt type continuously variable transmission 20 includes a first pulley 21 provided on the first pulley shaft 14 </ b> A, a second pulley 22 provided on the second pulley shaft 15 </ b> A, and a first pulley 21 and a second pulley 22. And an endless belt 23 wound around. The groove widths of the first pulley 21 and the second pulley 22 are increased or decreased in opposite directions by hydraulic pressure, and the gear ratio between the first pulley shaft 14A and the second pulley shaft 15A is continuously changed. The first pulley 21 includes a first fixed pulley 21A fixed to the first pulley shaft 14A, and a first movable pulley 21B that can approach and separate from the first fixed pulley 21A. The second pulley 22 includes a second fixed pulley 22A fixed to the second pulley shaft 15A, and a second movable pulley 22B that can approach and separate from the second fixed pulley 22A.

  Between the input shaft 13 (sub input shaft 13C) and the first output shaft 14 (first pulley shaft 14A), the rotational speed of the driving force from the main input shaft 13A is decelerated to reduce the driving force to a belt type continuously variable. A first transmission path 51 for transmitting to the transmission 20 is provided. The first transmission path 51 includes a first transmission drive gear 51A rotatably disposed on the input shaft 13 (sub input shaft 13C) and a first transmission driven gear 51B fixed to the first pulley shaft 14A. Have. The gear ratio between the first transmission drive gear 51A and the first transmission driven gear 51B is greater than 1. Therefore, the first transmission path 51 functions as a reduction gear train that transmits the driving force from the input shaft 13 while reducing the driving force.

  Between the input shaft 13 and the second output shaft 15 (second pulley shaft 15A), the rotational speed of the driving force from the input shaft 13 is increased to transmit the driving force to the belt-type continuously variable transmission 20. A second transmission path 52 is provided. The second transmission path 52 includes a second transmission drive gear 52A rotatably disposed on the input shaft 13 (sub-input shaft 13C) and a second transmission driven gear 52B fixed to the second pulley shaft 15A. Have. The gear ratio between the second transmission drive gear 52A and the second transmission driven gear 52B is smaller than 1. Therefore, the second transmission path 52 functions as a speed increasing gear train that increases the driving force from the input shaft 13 and transmits it to the belt-type continuously variable transmission 20.

  Between the input shaft 13 (sub input shaft 13C) and the first output shaft 14 (final drive shaft 14B), the rotational direction of the driving force from the sub input shaft 13C is reversed and transmitted to the first output shaft 14. A third transmission path 53 is provided. The third transmission path 53 includes a third transmission drive gear 53A rotatably disposed on the sub input shaft 13C, a third transmission driven gear 53C integrated with the clutch drum 64a of the fourth friction clutch 64, A third transmission idle gear 53B is provided between the three transmission drive gear 53A and the third transmission driven gear 53C. The third transmission idle gear 53B is rotatably supported on the reverse idle shaft 17. Due to the presence of the third transmission idle gear 53B, the third transmission path 53 functions as a gear train that transmits the driving force by reversing the rotational direction of the driving force.

  An intermediate transmission path between the first output shaft 14 (final drive shaft 14B) and the second output shaft 15 (second drive shaft 15B) for transmitting the driving force from the second drive shaft 15B to the final drive shaft 14B. 54 is disposed. The intermediate transmission path 54 includes an intermediate transmission drive gear 54A fixed to the second drive shaft 15B, an intermediate transmission driven gear 54C disposed on the final drive shaft 14B, an intermediate transmission drive gear 54A, and an intermediate transmission driven gear 54C. Intermediate transmission idle gear 54B disposed between the two. The intermediate transmission idle gear 54B is rotatably supported by the intermediate plate 102 and the torque converter case 101 via bearings BR7 and BR8. In FIG. 1, the intermediate transmission idle gear 54B and the intermediate transmission driven gear 54C are not adjacent to each other, but actually, the intermediate transmission idle gear 54B and the intermediate transmission driven gear 54C are adjacent to each other, and they mesh with each other. (Engaged). In the present embodiment, the intermediate transmission idle gear 54B is used as the intermediate transmission member that transmits the driving force from the intermediate transmission drive gear 54A to the intermediate transmission driven gear 54C. However, it is not always necessary to use a gear. For example, a configuration in which a driving force is transmitted by passing a chain between the second output shaft 15 and the first output shaft 14 may be used.

  A forward / reverse switching mechanism 70 is disposed on the sub input shaft 13C. The forward / reverse switching mechanism 70 is configured to selectively switch whether the driving force from the main input shaft 13A is transmitted to the second transmission path 52 or the third transmission path 53. As described above, the second transmission drive gear 52A and the third transmission drive gear 53A are rotatably supported on the sub input shaft 13C, and the sleeve 71 of the forward / reverse switching mechanism 70 is moved from the neutral position to the left in the drawing. When moved, the second transmission drive gear 52A and the sub input shaft 13C are coupled, and the driving force is transmitted from the input shaft 13 to the second transmission path 52 side. On the other hand, when the sleeve 71 of the forward / reverse switching mechanism 70 is moved from the neutral position to the right in the figure, the third transmission drive gear 53A and the sub input shaft 13C are coupled, and the driving force is transferred from the input shaft 13 to the third transmission path 53 side. Is transmitted to.

  The sleeve 71 of the forward / reverse switching mechanism 70 is driven leftward or rightward in the drawing by a hydraulic shift actuator 74.

  A final output mechanism 30 that outputs the driving force transmitted to the final drive shaft 14B is disposed downstream of the first output shaft 14 (final drive shaft 14B). The final output mechanism 30 is distributed by a final drive gear 31 disposed on the final drive shaft 14 </ b> B, a differential gear 33 having a final driven gear 32 that meshes with the final drive gear 31, and a differential gear 33. And a drive shaft 35 for transmitting the drive force to left and right drive wheels (not shown). In the present embodiment, the driving force from the second drive shaft 15B to the differential gear 33 of the final output mechanism 30 is transmitted to the final drive shaft 14B via the intermediate transmission path 54 and then transmitted to the final output mechanism 30. However, the present invention is not limited to this. Therefore, for example, as another example, the final drive gear is disposed on the second drive shaft 15B without the intermediate transmission path 54, and the driving force of the second drive shaft 15B is transmitted to the final output mechanism 30. May be.

  As described above, in the continuously variable transmission 1 according to the present embodiment, the intermediate plate 102 is assembled inside the transmission case 100, and the transmission case 100 has axially open end faces that protrude from the torque converter case 101. They are joined along the circumferential direction in a combined form. Further, the intermediate plate 102 can be used as a reference surface for alignment adjustment in the axial direction between the first pulley 21 and the second pulley 22. Accordingly, in FIG. 1, components related to the selection mechanism and the sub-transmission mechanism (hereinafter, “top-side sub-transmission mechanism”) positioned on the torque converter 12 side with respect to the intermediate plate 102, and the belt-type continuously variable transmission regarding the intermediate plate 102 The components related to the selection mechanism and the sub transmission mechanism (hereinafter referred to as “bottom side sub transmission mechanism”) positioned on the 20 side are assembled along the respective axes independently while reversing the assembled state of the transmission. It becomes possible. As a result, the transmission can be easily assembled. Hereinafter, the assembly of the continuously variable transmission 1 will be described.

FIG. 2 is an explanatory cross-sectional view of a main part showing an assembly process of the first pulley 21. In addition, about the hatching of a cross section, it shall be abbreviate | omitted suitably on account of description and it is the same after that. Further, the second pulley 22 to be combined is illustrated by a dotted line.
The first pulley 21 is assembled in a state of being erected on a first pulley bottom side stand 300 </ b> A provided on the first base plate 200. The first base plate 200 is an assembly jig and forms a bottom-side reference XY plane (a plane orthogonal to the axial direction) for each coordinate (relative position) of the first pulley 21 and the second pulley 22. The “bottom side” here means the first fixed pulley 21 </ b> A side of the first pulley 21 or the second movable pulley side 22 </ b> B of the second pulley 22 in the belt type continuously variable transmission 20.

  The first pulley bottom stand 300A and the second pulley bottom stand 300B are also assembly jigs, and the first pulley bottom stand 300A is based on the first base plate 200 (bottom side). While the coordinates (X, Y, Z) of the first pulley 21 are defined, the second pulley bottom stand 300B has the coordinates of the second pulley 22 with respect to the first base plate 200 (bottom side). (X, Y, Z) is defined. Accordingly, in this assembly process, the first pulley 21 is positioned with respect to the second pulley 22 with respect to the bottom side.

FIG. 3 is an explanatory cross-sectional view of a relevant part showing an assembly process of the second pulley 22. The first pulley 21 to be combined is illustrated by a dotted line.
The second pulley 22 is assembled in a state of being erected on a second pulley top side stand 310 </ b> B provided on the second base plate 210. The second transmission driven gear 52B constituting the second transmission path 52 has one end press-fitted into the second movable pulley 22B while being splined to the second pulley shaft 15A, and the other end by a washer W and a nut N via the bearing BR1. It is tightened and fixed to the second pulley shaft 15A.

  The second base plate 210 is an assembly jig similar to the first base plate 200, and is a top-side reference XY plane (perpendicular to the axial direction) for each coordinate (relative position) of the first pulley 21 and the second pulley 22. Plane). Here, the “top side” means the first movable pulley 21B side of the first pulley 21 or the second fixed pulley 22A side of the second pulley 22 in the belt type continuously variable transmission 20.

  Further, the second pulley top stand 310B and the first pulley top stand 310A determine the coordinates (X, Y, Z) of the second pulley 22 with respect to the second base plate 210 (top side). On the other hand, the first pulley top side stand 310A defines the coordinates (X, Y, Z) of the first pulley 21 when the second base plate 210 (top side) is used as a reference. Therefore, in this assembly process, the second pulley 22 is positioned with respect to the first pulley 21 with respect to the top side.

  As described above, the first pulley 21 is positioned with respect to the second pulley 22 with respect to the bottom side. Regarding the positioning on the bottom side and the positioning on the top side, both the XY coordinates are based on the same plane (a plane orthogonal to the axial direction), so the first pulley 21 shown in FIG. 2 and the second pulley 22 shown in FIG. Are combined in the form shown in FIG. 4, position adjustment (alignment adjustment) is not required for the XY coordinates. However, since the Z coordinate is based on a different reference plane, alignment adjustment is necessary for the Z coordinate. This alignment adjustment will be described later with reference to FIG.

  After the assembly process of the second pulley 22 is completed, an endless belt 23 is wound between the first pulley 21 and the second pulley 22 using a dedicated jig (not shown).

FIG. 4 is a cross-sectional explanatory view of a main part showing an assembling process of the first pulley 21 and the second pulley 22.
The first pulley 21 erected on the first pulley bottom stand 300A shown in FIG. 2 is fitted to the first pulley bottom stand 310A shown in FIG. 3, and the second pulley shown in FIG. The pulley bottom stand 300B is fitted to the second pulley 22 shown in FIG.

  Thereafter, the whole is turned upside down so that the first base plate 200 is grounded. Thereafter, the second base plate 210, the first pulley top stand 310A, and the second pulley top stand 310B are removed.

FIG. 5 is a cross-sectional explanatory view of a main part showing an assembly process of the intermediate plate 102 to the belt type continuously variable transmission 20.
As shown in FIG. 5, the alignment adjustment shim S selected in FIG. 6 to be described later is assembled to the second fixed pulley 22A. Thereafter, the intermediate plate 102 in which the bearings BR2 and BR3 are previously assembled is assembled to the first pulley 21 and the second pulley 22 so that the first pulley shaft 14A and the second pulley shaft 15A penetrate the bearings BR2 and BR3, respectively.

  Thereafter, the first transmission driven gear 51B constituting the first transmission path 51 is assembled to the first pulley shaft 14A via the leaf spring SP3 and tightened by the washer W3 and the nut N3. Thus, the first pulley shaft 14A is rotatably supported in a state where it is positioned with respect to the intermediate plate 102. On the other hand, by tightening the nut N2, the second pulley shaft 15A is rotatably supported while being positioned with respect to the intermediate plate 102. As a result, the first pulley 21 and the second pulley 22 are positioned with reference to the intermediate plate 102.

FIG. 6 is an explanatory diagram showing the alignment adjustment in the axial direction between the first pulley 21 and the second pulley 22.
As described above, for positioning in the Z direction (axial direction), the first pulley 21 is positioned with reference to the bottom side (first base plate 200), while the second pulley 22 is positioned on the top side (second base plate 210). Positioned with reference. Therefore, it is necessary to perform alignment adjustment with the same axial reference plane.

As a reference surface for positioning in the axial direction, for example, a surface facing the second fixed pulley 22A of the bearing BR2 of the intermediate plate 102 can be selected. Accordingly, in the axial alignment adjustment, for example, the winding diameter of the endless belt 23 in the first pulley 21 is set to φd1, and the winding diameter of the endless belt 23 in the second pulley 22 is set to φd2, respectively in FIG. The thickness of the alignment adjustment shim S so that the integrated values of A, B, C, D, E, F, and L shown in FIG. This is done by determining the value t. A, B, C, D, E, F, L, and G are the following dimension values.
A: Length from the reference surface of the bearing BR2 to the lower surface of the flange.
B: From the lower surface of the flange of the bearing BR2 (inside the fitting hole inner peripheral surface of the bearing BR2 of the intermediate plate 102, the Z-direction end surface 102A) to the upper surface of the flange of the bearing BR3 (inside of the inner peripheral surface of the fitting hole of the bearing BR3 of the intermediate plate 102, Length to the Z direction end face 102B).
C: The length from the upper surface of the flange of the bearing BR3 to the surface (the rear outer peripheral surface of the first piston 21C) in contact with the first transmission driven gear 51B of the first pulley 21.
D: Length from the rear outer peripheral surface of the first piston 21C to the rear inner peripheral surface of the first piston 21C corresponding to the outer peripheral surface thereafter.
E: Length from the rear inner peripheral surface of the first piston 21C to a predetermined position of the first movable pulley 21B.
F: Length from the predetermined position of the first movable pulley 21B to the predetermined position of the endless belt 23 (the saddle end of the element on the first fixed pulley 21A side).
L: Length of the element from the saddle end on the first fixed pulley 21A side to the saddle end on the first movable pulley 21B side.
G: Length from the rear outer peripheral surface (the surface facing the alignment adjustment shim S) of the second fixed pulley 22A to the saddle end of the element on the second fixed pulley 22A side.
The lengths can be determined to be negative when the direction from the start point to the end point is the top side (rightward in the figure), and to be positive when the direction is the bottom side (leftward in the figure).

FIG. 7 is an explanatory cross-sectional view of the relevant part showing the assembly process of the clutch drum 63 a of the third friction clutch 63.
Here, the clutch drum 63a constituting the third friction clutch 63 is assembled to the second pulley shaft 15A.

FIG. 8 is an explanatory cross-sectional view of a main part showing an assembly process of the sub input shaft 13C and the final drive shaft 14B.
Here, with respect to the auxiliary input shaft stand 320, the final drive shaft stand 330, and the second pulley shaft stand 340 in which the relative positional relationship between the auxiliary input shaft 13C, the final drive shaft 14B, and the second pulley shaft 15A is previously determined. The auxiliary input shaft 13C and the final drive shaft 14B are respectively attached. Thereafter, the first transmission drive gear 51A integrated with the clutch hub 61b of the first friction clutch 61 in advance is assembled to the sub input shaft 13C, while the intermediate transmission driven gear constituting the intermediate transmission path 54 is assembled to the final drive shaft 14B. Assemble 54C.

  After this step, the third base plate 220, the auxiliary input shaft stand 320, and the final drive shaft stand 330 replace the first base plate 200, the first pulley bottom side stand 300A, and the second pulley bottom side stand 300B. Used as an assembly jig.

FIG. 9 is a cross-sectional explanatory view of a main part showing an assembly process of the intermediate plate 102 to the sub input shaft 13C and the final drive shaft 14B.
Here, the bearing BR5 is assembled in the hole for the auxiliary input shaft 13C of the intermediate plate 102 shown in FIG. 7, the auxiliary input shaft 13C is passed through the hole, and the final drive shaft 14B is installed inside the first pulley shaft 14A. To penetrate. Further, the second pulley shaft 15A is assembled to the second pulley shaft stand 340.

FIG. 10 is an explanatory cross-sectional view of a main part showing an assembly process of the belt cover 103.
Here, the belt cover 103 shown in FIG. 11 is assembled to the intermediate plate 102. This belt cover 103 makes it possible to return a large amount of oil used for lubricating the endless belt 23 directly to an oil pan (not shown).

FIG. 12 is a cross-sectional explanatory view of a main part showing an assembling process of the forward / reverse switching mechanism 70. For convenience of explanation, the illustration of the peripheral portion of the second pulley shaft 15A is omitted.
Here, first, the hydraulic shift actuator 74 is assembled to the intermediate plate 102. The hydraulic shift actuator 74 is mounted in parallel to the auxiliary input shaft 13C and orthogonal to the intermediate plate 102.

  After the hydraulic shift actuator 74 is assembled to the intermediate plate 102, the third transmission drive gear 53A, the hub 73, the sleeve 71, and the second transmission drive gear 52A are sequentially assembled to the auxiliary input shaft 13C, and finally the shift fork 72 is assembled. The shift fork 72 is fixed to the front end portion of the hydraulic shift actuator 74 with a bolt B.

  The third transmission drive gear 53A, the hub 73, the sleeve 71, the second transmission drive gear 52A, and the shift fork 72 constitute a synchronous engagement device (synchro mechanism). Therefore, the forward / reverse switching mechanism 70 is a combination of the synchro mechanism and the hydraulic shift actuator 74. Therefore, by assembling the forward / reverse switching mechanism 70 on the intermediate plate 102 along the auxiliary input shaft 13C, the number of parts stacked tightly decreases, and as a result, there is less play between the parts and it is possible to assemble with high precision. It becomes.

FIG. 13 is an explanatory cross-sectional view of a main part showing an assembly process of the mission case 100.
Here, first, in the transmission assembly shown in FIG. 12, the reverse idle shaft 17 on which the third transmission driven gear 53 </ b> B is rotatably assembled in advance is assembled to the intermediate plate 102. Thereby, the assembly of the component parts related to the bottom side auxiliary transmission mechanism is completed. Thereafter, the transmission case 100 in which the bearing BR4 is assembled in advance is assembled in the transmission assembly.

  As is apparent from the drawing, the transmission case assembly and the transmission assembly are only fitted to the final drive shaft 14B, the auxiliary input shaft 13C, and the second pulley shaft 15A. Therefore, the transmission case 100 can be easily assembled.

  Further, as apparent from the figure, the intermediate plate 102 is assembled to the mission case 100 by the bolt B at the joint C2 inside the mission case 100. Thereby, the mission case 100 is positioned by the intermediate plate 102. The insertion direction of the bolt B is a direction parallel to the axis and orthogonal to the intermediate plate 102.

  Further, the reverse idle shaft 17 is fixed to the mission case 100 by a bolt B.

FIG. 14 is a cross-sectional explanatory view of a main part showing a reversing process of the transmission assembly.
Here, in order to assemble the components related to the top side auxiliary transmission mechanism in order along each axis, the assembly posture is reversed. First, the bearing BR4 attached to the tip of the final drive shaft 14B is fastened by the nut N. Thereafter, the cap 104 covering the tip is assembled to the mission case 100, and the transmission assembly is inverted so that the mission case 100 is grounded. Thereafter, the third base plate 220, the auxiliary input shaft stand 320, and the final drive shaft stand 330 are removed from the transmission assembly, and the components related to the top side auxiliary transmission mechanism are sequentially attached to the auxiliary input shaft 13C and the second pulley shaft 15A. Assembled.

FIG. 15 is an explanatory cross-sectional view of a main part showing an assembly process of the main input shaft 13A and the second drive shaft 15B.
Here, the second drive shaft 15B in which the intermediate transmission drive gear 54A has been assembled in advance is assembled rotatably inside the second pulley shaft 15A. Thereafter, the main input shaft 13A in which the first clutch drum 61a and the second clutch drum 62a are assembled in advance is assembled in the sub input shaft 13C in a rotatable manner.

FIG. 16 is a cross-sectional explanatory view of a main part showing an assembling process of the intermediate transmission idle gear 54B. For convenience of explanation, the peripheral portion of the second drive shaft 14B is not shown.
Here, the intermediate transmission idle gear 54B is assembled to the intermediate plate 102 via the bearing BR7. Thereby, the assembly of the component parts related to the top side auxiliary transmission mechanism is completed.

  As described above, in the continuously variable transmission 1 according to this embodiment, all the shafts except the drive shafts 35 and 35 of the final output mechanism 30 (the input shaft 13, the first output shaft 14, the second output shaft 15, the intermediate transmission idle gear). The shaft 54B and the reverse idle shaft 17) are supported by an intermediate plate 102. The intermediate plate 102 is attached to the inside of the transmission case 100 in a form that partitions the belt type continuously variable transmission 20 and the top side auxiliary transmission mechanism. Thus, in the assembly process of the continuously variable transmission 1, when the intermediate plate 102 is assembled to the first pulley 21 and the second pulley 22, the intermediate plate 102 is aligned in the axial direction of the first pulley 21 and the second pulley 22. It can be used as a reference plane for adjustment. As a result, the first pulley 21 and the second pulley 22 are positioned on the intermediate plate 102 with respect to the intermediate plate 102. That is, the alignment adjustment in the axial direction between the first pulley 21 and the second pulley 22 is completed in the assembly process of the intermediate plate 102. As a result, alignment adjustment with respect to the first pulley shaft 14A or the second pulley shaft 15A at the bottom end is not necessary. This eliminates the need to provide a side cover for alignment adjustment on the mission case 100.

  In the subsequent assembly process, the auxiliary input shaft 13C and the final drive shaft 14B may be assembled to the intermediate plate 102, and the components constituting the bottom side auxiliary transmission mechanism may be assembled in order along the respective axes. After the assembly of the side auxiliary transmission mechanism is completed, the assembly of the transmission is reversed, and similarly, the components constituting the top side auxiliary transmission mechanism are sequentially assembled along the respective axes. Finally, the torque converter is attached to the transmission case 100. Since the case 101 may be assembled, the transmission can be assembled easily.

  In addition, the intermediate plate 102 partitions the chamber containing the belt-type continuously variable transmission 20 and the chamber containing the top side auxiliary transmission mechanism, so that a large amount of oil used for lubricating the endless belt 23 can be removed. It is not scattered by the transmission mechanism. Further, by providing the belt cover 103 covering the endless belt 23 on the intermediate plate 102, it is possible to directly return the oil used for lubricating the endless belt 23 to the oil pan. Accordingly, it is possible to suitably prevent a part of the power transmitted to the transmission gear or the like in the bottom side subtransmission mechanism from being used for oil agitation.

  The forward / reverse switching mechanism 70 including the hydraulic shift actuator 74 is also fixed on the intermediate plate 102 along the sub input shaft 13C. As a result, the number of tightly stacked parts is reduced, and as a result, the backlash between the parts is reduced. As a result, the forward / reverse switching mechanism 70 can be assembled to the intermediate plate 102 with high accuracy.

  Further, since the fitting of the transmission case 100 on the bottom side of the transmission assembly is a fitting with respect to the auxiliary input shaft 13C, the final drive shaft 14B, and the second pulley shaft 15A, the transmission case 100 can be assembled to the intermediate plate 102. It becomes easy.

  In addition, regarding the oil supply to the shaft center, when no oil passage is provided in the transmission case 100, the fitting of the O-ring is eliminated at the joint C2 with the intermediate plate 102, and the transmission case 100 is assembled to the intermediate plate 102. It becomes even easier.

E drive source 1 continuously variable transmission 11 crankshaft 12 torque converter 13 input shaft 13A main input shaft 13C sub input shaft 14 first output shaft 14A first pulley shaft 14B final drive shaft 15 second output shaft 15A second pulley shaft 15B Second drive shaft 17 Reverse idle shaft 20 Belt type continuously variable transmission 21 First pulley 21A First fixed pulley 21B First movable pulley 22 Second pulley 22A Second fixed pulley 22B Second movable pulley 23 Endless belt 30 Final output mechanism 31 Final drive gear 32 Final driven gear 33 Differential gear 35 Drive shaft 51 First transmission path 51A First transmission drive gear 51B First transmission driven gear 52 Second transmission path 52A Second transmission drive gear 52B Second transmission driven gear 53 First Third transmission path 53A Third transmission drive gear 53B Third transmission Idle gear 53C Third transmission driven gear 54 Intermediate transmission path 54A Intermediate transmission drive gear 54B Intermediate transmission idle gear 54C Intermediate transmission driven gear 61 First friction clutch 62 Second friction clutch 63 Third friction clutch 64 Fourth friction clutch 70 Forward / reverse switching Mechanism 71 Sleeve 100 Mission case 101 Torque converter case 102 Intermediate case 103 Belt cover

Claims (4)

A driving force transmitting member that transmits driving force from the engine output shaft input to the input shaft to the driving pulley via a gear mechanism and is wound between the driven pulley and the driving pulley that are paired with the driving pulley. A continuously variable transmission that transmits the driving force to the driven pulley via:
A transmission case that houses the drive pulley and the driven pulley and rotatably supports one side of each rotation shaft of each pulley in the axial direction;
A power transmission mechanism case that houses a power transmission mechanism that transmits the driving force from the engine output shaft to the input shaft;
An intermediate plate for supporting the other side of the rotating shaft of the driving pulley and the driven pulley so as to be directly or indirectly rotatable and supporting the input shaft so as to be rotatable;
The intermediate plate is assembled to the inside of the transmission case, and the transmission case is assembled to the power transmission mechanism case with the axial end surfaces thereof being abutted against each other.   2. The continuously variable transmission according to claim 1, wherein the transmission includes a synchronous engagement device, and a shift actuator that drives a sleeve of the synchronous engagement device is disposed on a surface of the intermediate plate. Machine.   A cover member that covers the driving force transmission member is disposed on the intermediate plate at least in a circumferential direction of the driving force transmission member and at least in the range of the axial width of the driving pulley or the driven pulley. The continuously variable transmission according to claim 1 or 2.   4. An alignment adjusting member for adjusting an axial alignment between the driving pulley and the driven pulley is provided between the driving pulley or the driven pulley and the intermediate plate. The continuously variable transmission described in 1.

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