JP2016148434A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the assembling performance of a power transmission device while suppressing an increase of a manufacturing cost of the power transmission device.SOLUTION: A power transmission device includes: a radial bearing 147 which is arranged between a support part 112b of a cover member 112 and a sleeve 141 of a pump impeller 140; a drive sprocket 181 which rotates integrally with the sleeve 141, and is connected to an oil pump 17 arranged on a shaft different from an input shaft 20i of an automatic transmission via a chain 18; and a first washer 100 which is arranged between the support part 112b and the drive sprocket 181. The cover member 112 has a retention hole which extends to an axial direction from an end face of the support part 112b so as to communicate with an oil hole 112c which introduces oil to the radial bearing 147, and a first washer 100 has a retention protrusion 103 which protrudes from a ring part 101, is inserted into the retention hole, and engaged with an internal peripheral face of the oil hole 112c.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a power transmission device that includes a torque converter, a transmission, and a case that houses the torque converter and the transmission.

  Conventionally, as this type of power transmission device, an oil pump disposed at a position radially spaced from a rotating shaft of a torque converter, a first sprocket that rotates around the rotating shaft, and a second sprocket that drives the oil pump And an oil pump drive mechanism including a chain is known (see, for example, Patent Document 1). In this power transmission device, a first bush is provided between the axially extending portion of the torque converter sleeve extended from the pump impeller of the torque converter and the stator shaft, and between the first sprocket and the stator shaft. A second bush is provided. A disc spring is provided between the first sprocket and the torque converter housing, and a thrust bearing is provided between the first sprocket and the cover. As a result, the first sprocket is positioned in the axial direction by the disc spring and the thrust bearing.

JP 2005-325979 A

  In the conventional power transmission device, a disc spring is disposed between the first sprocket and the torque converter housing. However, in view of the assemblability of the power transmission device, the disc spring is locked to the torque converter housing, for example. It is preferable that it is (prevented). However, in order to lock the disc spring to the torque converter housing or the like, it is necessary to change the design of the member or perform additional work, which may increase the manufacturing cost of the power transmission device.

  Then, this invention makes it the main objective to improve the assembly property of the said power transmission device, suppressing the increase in the manufacturing cost of a power transmission device.

  A power transmission device according to the present invention includes a fluid transmission device having a pump impeller and a turbine runner, a transmission, and a case that houses the fluid transmission device and the transmission. A cover member having an annular wall portion fixed to the case so as to be positioned between the transmission, a cylindrical portion extending in an axial direction from an inner periphery of the annular wall portion, and the cylinder of the cover member A bearing that is disposed in a gap between an inner peripheral surface of the shaped portion and an outer peripheral surface of a sleeve that extends in an axial direction from the pump impeller toward the transmission, and rotatably supports the pump impeller; A driving member that rotates integrally with the sleeve of the pump impeller and that is connected to an oil pump disposed on a shaft different from the input shaft of the transmission, and the cylindrical portion of the cover member and the front An oil hole penetrating an upper portion of the cylindrical portion of the cover member so as to communicate with the gap in which the bearing is disposed. And a retaining hole extending in the axial direction so as to communicate with the oil hole from the end surface on the drive member side of the tubular portion, and the washer abuts against the end surface of the tubular portion; It has a retaining projection that protrudes in the axial direction from the ring portion and is inserted into the retaining hole of the cover member so as to be engageable with the inner peripheral surface of the oil hole.

  The power transmission device includes a cover member having an annular wall portion fixed to the case so as to be positioned between the fluid transmission device and the transmission, and a cylindrical portion extending in an axial direction from the inner periphery of the annular wall portion. The bearing is disposed in a gap between the inner peripheral surface of the cylindrical portion of the cover member and the outer peripheral surface of the sleeve extending in the axial direction from the pump impeller toward the transmission, and rotatably supports the pump impeller. And a drive member that rotates integrally with a sleeve of the pump impeller and is connected to an oil pump that is disposed on a shaft different from the input shaft of the transmission, and a cylindrical portion of the cover member and the drive member in the axial direction. And a washer disposed between them. Further, the cover member has an oil hole that penetrates through the upper portion of the cylindrical portion of the cover member so as to communicate with a gap in which the bearing is disposed, and a shaft that communicates with the oil hole from the end surface on the drive member side of the cylindrical portion. And a retaining hole extending in the direction. Further, the washer is a retaining portion inserted into the retaining hole of the cover member so as to be able to engage with the inner peripheral surface of the oil hole while protruding from the ring portion in the axial direction while being in contact with the end surface of the cylindrical portion. And a protrusion. In this way, by connecting the retaining hole formed in the cylindrical part of the cover member and the oil hole through which the lubricating oil of the bearing arranged between the cylindrical part and the sleeve of the pump impeller flows, It is no longer necessary to form a dedicated hole in the cylindrical portion with an inner peripheral surface that engages with the retaining protrusion, and an increase in the manufacturing cost of the power transmission device can be suppressed. Further, the stopper protrusion of the washer inserted into the stopper hole engages with the inner peripheral surface of the oil hole, so that the washer is prevented from dropping from the cover member. Accordingly, the cover member and the washer can be attached to the case at the same time, and the assemblability of the power transmission device can be improved. As a result, it is possible to improve the assemblability of the power transmission device while suppressing an increase in manufacturing cost of the power transmission device.

It is a schematic block diagram of the power transmission device by this invention. 2 is an operation table showing the relationship between each gear position and the operating states of clutches and brakes in the transmission of the power transmission device of FIG. 1. FIG. 2 is a velocity diagram showing a ratio of a rotational speed of each rotary element to an input rotational speed in the transmission of the power transmission device of FIG. 1. It is an expanded sectional view which shows the power transmission device by this invention. It is a principal part expanded sectional view which shows the cover member contained in the power transmission device by this invention. It is a perspective view which shows the cover member contained in the power transmission device by this invention. It is a top view which shows the cover member contained in the power transmission device by this invention. It is a perspective view which shows the 1st washer contained in the power transmission device by this invention. It is a principal part expanded sectional view which shows the cover member and 1st washer which are included in the power transmission device by this invention.

  Next, the form for implementing this invention is demonstrated, referring drawings.

  FIG. 1 is a schematic configuration diagram of a power transmission device 10 according to the present invention. A power transmission device 10 shown in the figure is connected to a crankshaft of an engine (internal combustion engine) (not shown) and / or a rotor of an electric motor as a drive source mounted vertically in a front portion of a rear wheel drive vehicle. Power (torque) from an engine or the like can be transmitted to left and right rear wheels (drive wheels) (not shown). As shown in the figure, the power transmission device 10 shifts the power transmitted from the transmission case (stationary member) 11, the starting device (fluid transmission device) 12, the oil pump 17, the engine, etc. to the input shaft (input member) 20i. And an automatic transmission 20 that transmits the output shaft (output member) 20o.

  The starting device 12 includes a front cover 13 connected to a crankshaft of an engine and / or a rotor of an electric motor via a drive plate or the like (not shown), and an input side having a pump shell closely fixed to the front cover 13. Pump impeller 140, output-side turbine runner 142 connected to input shaft 20i of automatic transmission 20, pump impeller 140, and hydraulic oil (ATF) from turbine runner 142 to pump impeller 140 disposed inside turbine runner 142 A torque converter (fluid transmission) having a stator 143 that rectifies the flow of the motor, a one-way clutch 144 that restricts the rotational direction of the stator 143 to one direction, and the like. The starting device 12 may include a fluid coupling that does not have the stator 143.

  Further, the starting device 12 connects the front cover 13 connected to the crankshaft of the engine and the like and the input shaft 20i of the automatic transmission 20 to each other, and releases the connection between the lockup clutch 15 and the front cover 13. And a damper mechanism 16 that attenuates vibration between the input shaft 20 i of the automatic transmission 20. In the present embodiment, the lockup clutch 15 is configured as a multi-plate friction type hydraulic clutch having a plurality of friction engagement plates (friction plates and separator plates). However, the lockup clutch 15 may be a single plate friction type hydraulic clutch.

  The oil pump 17 includes a rotor 170 coupled to the pump impeller 140 of the starting device 12 via the chain 18, an external gear (drive gear) 171 having a plurality of external teeth and rotating integrally with the rotor 170, an external gear An internal gear (driven gear) 172 that has a plurality of internal teeth that are one more than the total number of external teeth that mesh with the external teeth of the tooth gear 171 and is arranged eccentrically with respect to the external gear 171. The oil pump 17 is driven by the power from the engine transmitted through the chain 18 and the like, sucks hydraulic oil stored in an oil pan (not shown), and pumps it to a hydraulic control device (not shown). In the present embodiment, the oil pump 17 is disposed in the lower part of the transmission case 11 so that the rotor 170 is located on a different shaft from the input shaft 20 i of the automatic transmission 20. As a result, the outer diameters of the rotor 170, the external gear 171 and the internal gear 172 can be reduced as compared with the case where the rotor 170 is arranged coaxially with the input shaft 20i. Can be achieved.

  The automatic transmission 20 is configured as a 10-speed transmission, and as shown in FIG. 1, an output shaft connected to the left and right rear wheels via an input shaft 20i, a differential gear (not shown), and a drive shaft. In addition to 20o, a single pinion type first planetary gear 21 and a second planetary gear 22 arranged in the axial direction of the automatic transmission 20 (input shaft 20i and output shaft 20o), a double pinion type planetary gear and a single And a Ravigneaux type planetary gear mechanism 25 as a compound planetary gear train configured by combining with a pinion type planetary gear. Further, the automatic transmission 20 includes a clutch C1 (first clutch) as a first engagement element and a clutch C2 (second clutch) as a second engagement element for changing the power transmission path from the input shaft 20i to the output shaft 20o. A second clutch), a clutch C3 (third clutch) as a third engagement element, a clutch C4 (fourth clutch) as a fourth engagement element, a brake B1 (first brake) as a fifth engagement element, and A brake B2 (second brake) as a sixth engagement element is included.

  In the present embodiment, the first and second planetary gears 21 and 22 and the Ravigneaux planetary gear mechanism 25 are connected to the Ravigneaux planetary gear mechanism 25 and the second planetary gear 22 from the starting device 12, that is, the engine side (left side in FIG. 1). The first planetary gear 21, that is, the single pinion planetary gear constituting the Ravigneaux planetary gear mechanism 25, the double pinion planetary gear constituting the Ravigneaux planetary gear mechanism 25, the second planetary gear 22, and the first planetary gear 21. It arrange | positions in the transmission case 11 so that it may rank in order. Thereby, the Ravigneaux type planetary gear mechanism 25 is arrange | positioned at the front part side of a vehicle so that the starting apparatus 12 may be adjoined. The first planetary gear 21 is disposed on the rear side of the vehicle so as to be close to the output shaft 20o. Further, the second planetary gear 22 is disposed between the Ravigneaux type planetary gear mechanism 25 and the first planetary gear 21 in the axial direction of the input shaft 20 i, the output shaft 20 o and the like.

  The first planetary gear 21 includes a first sun gear 21s that is an external gear, a first ring gear 21r that is an internal gear disposed concentrically with the first sun gear 21s, and a first sun gear 21s and a first ring gear 21r, respectively. And a first carrier 21c that holds the plurality of first pinion gears 21p so as to freely rotate (rotate) and revolve. In the present embodiment, the gear ratio λ1 of the first planetary gear 21 (the number of teeth of the first sun gear 21s / the number of teeth of the first ring gear 21r) is set to λ1 = 0.277, for example.

  As shown in FIG. 1, the first carrier 21c of the first planetary gear 21 is always connected (fixed) to an intermediate shaft (intermediate shaft) 20m of the automatic transmission 20 connected to the input shaft 20i. Thus, when power is transmitted from the engine to the input shaft 20i, power from the engine is constantly transmitted to the first carrier 21c via the input shaft 20i and the intermediate shaft 20m. The first carrier 21c functions as an input element of the first planetary gear 21 when the clutch C4 is engaged, and idles when the clutch C4 is released. Further, the first ring gear 21r functions as an output element of the first planetary gear 21 when the clutch C4 is engaged.

  The second planetary gear 22 includes a second sun gear 22s that is an external gear, a second ring gear 22r that is an internal gear disposed concentrically with the second sun gear 22s, and a second sun gear 22s and a second ring gear 22r, respectively. And a second carrier (planetary carrier) 22c that holds the plurality of second pinion gears 22p so that they can rotate (rotate) and revolve freely. In the present embodiment, the gear ratio λ2 of the second planetary gear 22 (the number of teeth of the second sun gear 22s / the number of teeth of the second ring gear 22r) is determined to be, for example, λ2 = 0.244.

  As shown in FIG. 1, the second sun gear 22s of the second planetary gear 22 is integrated (always connected) with the first sun gear 21s of the first planetary gear 21, and is always integrated with the first sun gear 21s (and Rotate or stop on the same axis. However, the first sun gear 21s and the second sun gear 22s may be configured separately and always connected via a connecting member (first connecting member) (not shown). The second carrier 22c of the second planetary gear 22 is always connected to the output shaft 20o, and always rotates or stops integrally (and coaxially) with the output shaft 20o. As a result, the second carrier 22 c functions as an output element of the second planetary gear 22. Further, the second ring gear 22 r of the second planetary gear 22 functions as a fixable element of the second planetary gear 22.

  The Ravigneaux type planetary gear mechanism 25 includes a third sun gear 23s and a fourth sun gear 24s that are external gears, a third ring gear 23r that is an internal gear disposed concentrically with the third sun gear 23s, and a third sun gear 23s. A plurality of third pinion gears (short pinion gears) 23p, a plurality of fourth pinion gears (long pinion gears) 24p meshing with the fourth sun gear 24s and the plurality of third pinion gears 23p and meshing with the third ring gear 23r. And a third carrier 23c that holds the third pinion gear 23p and the plurality of fourth pinion gears 24p so as to freely rotate (rotate) and revolve.

  Such Ravigneaux planetary gear mechanism 25 is a compound planetary gear train configured by combining a double pinion planetary gear (third planetary gear) and a single pinion planetary gear (fourth planetary gear). That is, the third sun gear 23s, the third carrier 23c, the third and fourth pinion gears 23p and 24p, and the third ring gear 23r of the Ravigneaux planetary gear mechanism 25 constitute a double pinion type third planetary gear. Further, the fourth sun gear 24s, the third carrier 23c, the fourth pinion gear 24p, and the third ring gear 23r of the Ravigneaux type planetary gear mechanism 25 constitute a single pinion type fourth planetary gear. In the present embodiment, the Ravigneaux type planetary gear mechanism 25 has a gear ratio λ3 of the double pinion type third planetary gear (the number of teeth of the third sun gear 23s / the number of teeth of the third ring gear 23r), for example, λ3 = The gear ratio λ4 of the single pinion type fourth planetary gear (the number of teeth of the fourth sun gear 24s / the number of teeth of the third ring gear 23r) is, for example, λ4 = 0.581. The

  Of the rotating elements constituting the Ravigneaux type planetary gear mechanism 25 (third and fourth planetary gears), the fourth sun gear 24s is an element that can be fixed to the Ravigneaux type planetary gear mechanism 25 (the second fixing of the automatic transmission 20). Function as a possible element). Further, as shown in FIG. 1, the third carrier 23 c is always connected (fixed) to the input shaft 20 i, and the first planetary gear 21 is connected via an intermediate shaft 20 m as a connecting member (second connecting member). Always connected to the first carrier 21c. As a result, when power is transmitted from the engine to the input shaft 20i, power from the engine is constantly transmitted to the third carrier 23c via the input shaft 20i. Therefore, the third carrier 23 c functions as an input element of the Ravigneaux planetary gear mechanism 25. The third ring gear 23r functions as a first output element of the Ravigneaux planetary gear mechanism 25, and the third sun gear 23s functions as a second output element of the Ravigneaux planetary gear mechanism 25.

  The clutch C1 mutually connects the first sun gear 21s of the first planetary gear 21 and the second sun gear 22s of the second planetary gear 22 and the third ring gear 23r, which is the first output element of the Ravigneaux type planetary gear mechanism 25, to each other. It connects and cancels both connections. The clutch C2 mutually connects the first sun gear 21s of the first planetary gear 21 and the second sun gear 22s of the second planetary gear 22 and the third sun gear 23s, which is the second output element of the Ravigneaux type planetary gear mechanism 25, to each other. It connects and cancels both connections. The clutch C3 connects and disconnects the second ring gear 22r of the second planetary gear 22 and the third ring gear 23r, which is the first output element of the Ravigneaux type planetary gear mechanism 25, to each other. The clutch C4 connects the first ring gear 21r, which is the output element of the first planetary gear 21, and the output shaft 20o to each other and releases the connection between them.

  The brake B1 fixes (connects) the fourth sun gear 24s, which can be fixed to the Ravigneaux type planetary gear mechanism 25, to the transmission case 11 as a stationary member in a non-rotatable manner, and the fourth sun gear 24s to the transmission case 11. In contrast, it is free to rotate. The brake B2 fixes (connects) the second ring gear 22r, which is a fixable element of the second planetary gear 22, to the transmission case 11 so as not to rotate, and the second ring gear 22r to the transmission case 11 as a stationary member. And free to rotate.

  In the present embodiment, as the clutches C1 to C4, a hydraulic servo including a piston, a plurality of friction engagement plates (friction plates and separator plates), an engagement oil chamber to which hydraulic oil is supplied, a centrifugal hydraulic pressure cancellation chamber, and the like. A multi-plate friction type hydraulic clutch (friction engagement element) having the above is adopted. Further, as the brakes B1 and B2, a multi-plate friction hydraulic brake having a hydraulic servo including a piston, a plurality of friction engagement plates (friction plates and separator plates), an engagement oil chamber to which hydraulic oil is supplied, and the like. Is adopted. The clutches C1 to C4 and the brakes B1 and B2 operate when hydraulic oil is supplied and discharged by the hydraulic control device.

  FIG. 2 shows an operation table showing the relationship between the respective shift stages of the automatic transmission 20 and the operating states of the clutches C1 to C4 and the brakes B1 and B2. FIG. 3 shows the rotational speed of the input shaft 20i in the automatic transmission 20 ( The speed diagram which shows ratio of the rotational speed of each rotation element with respect to (input rotational speed) is shown. The automatic transmission 20 provides the forward speed and the reverse speed from the first speed to the tenth speed by setting the clutches C1 to C4 and the brakes B1 and B2 to the states shown in the operation table of FIG.

  In addition, the first and second planetary gears 21 and 22 and the ten rotating elements of the Ravigneaux type planetary gear mechanism 25 (however, the first sun gear 21s and the second sun gear 22s are always coupled, A total of nine rotating elements) are arranged in the order shown in the figure from the left side in FIG. 3 at intervals according to these gear ratios λ1, λ2, λ3, and λ4. According to such an arrangement order on the speed diagram, in the present embodiment, the first sun gear 21s is the first rotating element of the automatic transmission 20, the first carrier 21c is the second rotating element of the automatic transmission 20, The first ring gear 21r is the third rotating element of the automatic transmission 20. Further, the second sun gear 22s is the fourth rotating element of the automatic transmission 20, the second carrier 22c is the fifth rotating element of the automatic transmission 20, and the second ring gear 22r is the fourth rotating element of the automatic transmission 20. . Further, the fourth sun gear 24s is the seventh rotating element of the automatic transmission 20, the third carrier 23c is the eighth rotating element of the automatic transmission 20, and the third ring gear 23r is the ninth rotating element of the automatic transmission 20. The third sun gear 23 s is the tenth rotating element of the automatic transmission 20.

  The gear ratios λ1 to λ4 of the first and second planetary gears 21 and 22 and the third and fourth planetary gears are not limited to those described above. In the automatic transmission 20, at least one of the clutches C1 to C4 and the brakes B1 and B2 may be a meshing engagement element such as a dog clutch or a dog brake. For example, in the automatic transmission 20, even when a dog brake is employed as the brake B2 that is continuously engaged when the first forward speed is established to the fourth forward speed and is engaged when the reverse speed is formed. Good. Further, in the automatic transmission 20, at least one of the first and second planetary gears 21 and 22 may be a double pinion type planetary gear, and the Ravigneaux type planetary gear mechanism 25 is, for example, a Simpson type or a CR- It may be replaced with a compound planetary gear train such as a CR type. Further, the automatic transmission 20 described above may be modified to a transmission mounted on a front wheel drive vehicle.

  FIG. 4 is an enlarged cross-sectional view showing the configuration around the starting device 12 and the oil pump 17 of the power transmission device 10. As shown in the figure, the transmission case 11 that houses the starting device 12 and the automatic transmission 20 is positioned between the cylindrical case main body 110 and the starting device 12 (fluid transmission device) and the automatic transmission 20. The front support (support member) 111 fastened (fixed) to the case main body 110 and the cover member fastened (fixed) to the case main body 110 together with the front support 111 so as to cover the front support 111 from the starting device 12 side. 112, and a center support 115 (see FIG. 1) fastened (fixed) to the case main body 110 so as to be positioned between the Ravigneaux type planetary gear mechanism 25 and the second planetary gear 22 (and the first planetary gear 21). including.

  As shown in FIG. 4, the front support 111 includes an annular wall portion 111 a fastened to the case body 110 and a cylindrical portion 111 b extending in the axial direction of the input shaft 20 i from the wall portion 111 a toward the starting device 12. Have. Further, the cover member 112 is fastened to the transmission case 11 so as to be positioned between the starting device 12 and the automatic transmission 20 in the axial direction, and extends in the radial direction. And a short cylindrical support portion (tubular portion) 112b extending in the axial direction from the inner periphery. In the present embodiment, the case main body 110, the front support 111, the cover member 112, and the center support 115 are formed by casting, for example, an aluminum alloy.

  As shown in FIG. 4, a space 11x is defined between the wall portion 111a of the front support 111 and the annular wall portion 112a of the cover member 112 in the axial direction. An opening 111o having a relatively large opening area that communicates the space 11x and the inside of the case main body 110 in which the automatic transmission 20 is disposed is formed. The front support 111 is fastened with a pump body 173 that defines a gear housing chamber that houses the external gear 171 and the internal gear 172 of the oil pump 17, and a pump cover 174 is fastened to the pump body 173. Is done. The pump body 173 may be integrated with the front support 111, and the pump body 173 and the pump cover 174 may be integrated.

  Furthermore, a hollow stator shaft 145 made of steel (iron alloy) is press-fitted (fixed) into the cylindrical portion 111b of the front support 111 so as to surround the input shaft 20i. The tip of the stator shaft 145 is spline-fitted into the inner race of the one-way clutch 144 of the starting device 12. As a result, the stator 143 is connected to the stator shaft 145 via the one-way clutch 144. A bush (bearing) is interposed between the inner peripheral surface of the stator shaft 145 and the outer peripheral surface of the input shaft 20 i, and the ring member 146 is fitted to the stator shaft 145. The ring member 146 is formed of a steel material (iron alloy), and is press-fitted and fixed to the outer peripheral surface of the stator shaft 145 so that one end is in contact with the tip of the cylindrical portion 111b of the front support 111. A seal mounting groove is formed on the outer peripheral surface of the ring member 146, and a seal member such as a seal ring is disposed in the seal mounting groove so as to be in sliding contact with the inner peripheral surface of the cylindrical portion 141b of the sleeve 141. Is done. Thereby, it is possible to restrict the hydraulic oil in the fluid transmission chamber of the starting device 12 from leaking to the front support 111 side by the seal member disposed between the ring member 146 and the cylindrical portion 141b of the sleeve 141. .

  As shown in FIG. 4, the pump impeller 140 constituting the torque converter of the starting device 12 includes a pump shell 140a that is tightly fixed to the front cover 13, and a plurality of pump blades 140b disposed on the inner surface of the pump shell 140a. And a sleeve 141 closely joined to the inner peripheral portion of the pump shell 140a by welding. The sleeve 141 is formed of a steel material (iron alloy) similarly to the pump shell 140a and the pump blade 140b, and has an annular flange portion 141a joined to the inner peripheral portion of the pump shell 140a and the inner periphery of the flange portion 141a. And a cylindrical portion 141b extending in the axial direction of the input shaft 20i from the portion toward the automatic transmission 20 side (right side in FIG. 4).

  In the cylindrical portion 141b of the sleeve 141, the cylindrical portion 111b of the front support 111 is fitted (inserted) from the automatic transmission 20 side (the right side in FIG. 4), and the outer peripheral surface of the cylindrical portion 141b and the cover member 112 are inserted. A radial bearing 147 is disposed in the gap with the inner peripheral surface of the support portion 112b. Thereby, the sleeve 141, that is, the pump impeller 140 is rotatably supported by the front support 111 and the cover member 112, that is, the transmission case 11 via the radial bearing 147. Further, an oil seal 148 is disposed between the outer peripheral surface of the cylindrical portion 141b and the inner peripheral surface of the support portion 112b so as to be closer to the flange portion 141a of the sleeve 141 than the radial bearing 147.

  Further, the free end portion (the right end portion in FIG. 4, the end portion on the automatic transmission 20 side) of the cylindrical portion 141b of the sleeve 141 is attached to a boss portion of a drive sprocket 181 as a drive member around which the chain 18 is wound. A plurality of (for example, two) engaging protrusions 141c that are respectively fitted in the formed engaging grooves are formed. As shown in FIG. 4, the drive sprocket 181 is rotatably supported by the cylindrical portion 111b of the front support 111 so as to be positioned between the support portion 112b of the cover member 112 and the wall portion 111a of the front support 111. And is connected to the sleeve 141 (pump impeller 140) so as to rotate integrally through the engaging protrusion 141c and the like. As a result, the external gear 171 and the internal gear 172 of the oil pump 17 are transmitted by the power from the engine transmitted through the pump impeller 140, the sleeve 141, the drive sprocket 181, the chain 18 and the driven sprocket 182 fixed to the rotor 170. Can be rotated.

  As shown in FIGS. 4, 6, and 7, one oil hole that penetrates the support portion 112 b is provided in the upper portion of the support portion 112 b of the cover member 112 so as to guide hydraulic oil for lubrication to the radial bearing 147. 112c is formed. The oil hole 112c extends obliquely so as to approach the flange portion 141a of the sleeve 141 from the outer peripheral side to the inner peripheral side of the support portion 112b. In this embodiment, as shown in FIG. 5, the oil hole 112c communicates with and supports a large-diameter oil collecting hole 112d that opens radially outward on the outer peripheral surface of the support portion 112b. A communicating hole 112e having a smaller diameter than the oil collecting hole 112d opened on the inner peripheral surface of the portion 112b. The communication hole 112e that constitutes the oil hole 112c opens between the radial bearing 147 and the oil seal 148 in the axial direction, as shown in the figure. As a result, the oil hole 112c communicates with the gap in which the radial bearing 147 is disposed.

  Further, as shown in FIGS. 4, 6 and 7, the annular wall portion 112a of the cover member 112 has a starting device from the automatic transmission 20 side (the right side in FIG. 4) above the oil hole 112c of the support portion 112b. A recess 112f is formed so as to be recessed toward the 12th side (left side in FIG. 4). In addition, the annular wall 112a has a first protrusion 112g extending along one side edge (left side in FIG. 7) of the recess 112f and a second protrusion 112h extending along the upper edge of the recess 112f. Is formed.

  The first and second projecting portions 112g and 112h are at least from the end surface on the front support 111 side of the support portion 112b from the starting device 12 side (left side in FIG. 4) toward the automatic transmission 20 side (right side in FIG. 4). Also protrudes from the annular wall 112a so as to be close to the wall 111a. In the present embodiment, the rotation direction of the pump impeller 140 and the input shaft 20i when the vehicle moves forward is the counterclockwise direction in FIG. 7 (see the bold arrow in FIG. 7) when viewed from the rear side of the power transmission device 10. The first protrusion 112g extends along the front side edge in the rotational direction of the pump impeller 140 and the like of the recess 112f.

  Further, the first washer 100 is disposed between the support portion 112b of the cover member 112 and the drive sprocket 181 in the axial direction, and between the drive sprocket 181 and the wall portion 111a of the front support 111 in the axial direction, A second washer 200 is disposed. In the present embodiment, the first and second washers 100 and 200 are formed of a resin material including, for example, nylon 66 or the like.

  As shown in FIG. 8, the first washer 100 includes an annular ring portion 101. From one surface of the ring portion 101, an annular ring portion that supports the surface of the drive sprocket 181 on the cover member 112 side in the axial direction. The support part 102 is extended. On the surface of the support portion 102, a plurality of oil grooves that allow the flow of hydraulic oil as a lubricating medium are formed at regular intervals in the circumferential direction.

  Further, as shown in FIGS. 4 and 8, the first washer 100 has one retaining protrusion 103 that protrudes in the axial direction from the surface of the ring part 101 opposite to the drive sprocket 181. In the present embodiment, the retaining projection 103 is composed of two pins 103a that can be elastically deformed along the radial direction of the ring portion 101, and one pin 103a located on the radially outer side has a diameter as shown in the figure. A protrusion 103b that protrudes outward in the direction is formed. Further, as shown in FIGS. 4 and 8, the first washer 100 has a plurality of protrusions protruding in the axial direction from the surface opposite to the drive sprocket 181 of the ring portion 101 at a position spaced apart from the retaining protrusion 103 in the circumferential direction. (In this embodiment, two) anti-rotation protrusions 104 are provided. In this embodiment, the rotation prevention projection part 104 is formed in the column shape (round bar shape). In addition, the first washer 100 has an extending portion 105 that extends radially outward from a part of the outer periphery of the ring portion 101. The extending portion 105 extends upward in FIG. 8 from the vicinity of the base end of the retaining projection 103 and is formed to be narrower than the width of the lower portion of the recess 112 f formed in the cover member 112.

  On the other hand, as shown in FIGS. 4 to 6, the support 112b of the cover member 112 has an oil hole 112c (oil collecting hole 112d) from the end surface on the drive sprocket 181 side (the right side in FIG. 4, ie, the automatic transmission 20 side). And one retaining hole 112i extending in the axial direction so as to communicate with the communication hole 112e). Further, the support portion 112b of the cover member 112 has a plurality of (this embodiment) extending in the axial direction at intervals from the end surface of the drive sprocket 181 of the support portion 112b at a position spaced in the circumferential direction from the retaining hole 112i. Then, two anti-rotation holes 112j (see FIG. 6) are formed.

  The retaining protrusion 103 of the first washer 100 is inserted into the retaining hole 112 i of the cover member 112, and the protrusion 103 b formed on one pin 103 a that constitutes the retaining protrusion 103 is an oil as shown in FIG. 9. It becomes possible to engage with the inner peripheral surface of the hole 112c (oil collecting hole 112d). Further, each rotation preventing projection 104 of the first washer 100 is fitted (inserted) into the corresponding rotation preventing hole 112j of the cover member 112. Accordingly, the first washer 100 is snapped to the support portion 112b so as not to rotate with respect to the cover member 112. In addition, the first washer 100 is prevented from being detached from the cover member 112 by engaging the protrusion 103b of the retaining protrusion 103 with the inner peripheral surface of the oil hole 112c (oil collecting hole 112d). Become. Further, when the first washer 100 is attached to the support portion 112b, the ring portion 101 abuts against the end surface of the support portion 112b on the drive sprocket 181 side, and the extension portion 105 of the first washer 100 is shown in FIGS. 7 and FIG. 9, it projects upward from the outer peripheral surface of the support portion 112b and faces the annular wall portion 112a through the recess 112f of the cover member 112.

  As shown in FIG. 4, the second washer 200 includes an annular ring portion 201. From one surface of the ring portion 201, an annular ring portion that supports the surface on the front support 111 side of the drive sprocket 181 in the axial direction. The support part is extended. Also on the surface of the support portion of the second washer 200, a plurality of oil grooves that allow the flow of hydraulic oil as a lubricating medium are formed at regular intervals in the circumferential direction. Further, as shown in FIG. 4, the second washer 200 has a plurality of anti-rotation protrusions 204 protruding in the axial direction at intervals in the circumferential direction from the surface of the ring part 201 opposite to the drive sprocket 181. . Each detent projection 204 is fitted in a detent hole formed in the wall 111 a of the front support 111. Accordingly, the second washer 200 is disposed between the wall 111a and the drive sprocket 181 so as not to rotate with respect to the front support 111.

  In the power transmission device 10 configured as described above, the hydraulic oil stays in the transmission case 11 when the oil pump 17 is driven by the power from the engine transmitted via the drive sprocket 181 or the chain 18 or the like. Is scraped up by the chain 18 as shown by the dotted line in FIG. When the power from the engine is transmitted to the input shaft 20i and the rotating element of the automatic transmission 20 rotates, the lubricating / cooling hydraulic oil supplied to the automatic transmission 20 scatters as the rotating element rotates. A part of the hydraulic oil scattered near the front support 111 enters the space 11x between the front support 111 and the cover member 112 through the opening 111o formed in the wall 111a.

  Then, the working oil scooped up by the chain 18 with the rotation of the drive sprocket 181 and the working oil scattered into the space 11x with the rotation of the rotating element of the automatic transmission 20 are formed in the cover member 112. The recessed portion 112f hits the first protruding portion 112g extending along the side edge on the front side in the rotational direction of the pump impeller 140, and is collected in the recessed portion 112f. As a result, a large amount of hydraulic oil is collected in the recess 112f and can flow down from the recess 112f to the oil hole 112c to be used for lubrication of the radial bearing 147. Therefore, the hydraulic control oil is supplied radially from the hydraulic control device. There is no need to supply the bearing 147 directly. As a result, in the power transmission device 10, it is possible to satisfactorily lubricate the radial bearing 147 that supports the pump impeller 140 without increasing the load of the oil pump 17.

  Further, the hydraulic oil scattered into the space 11x with the rotation of the rotary element of the automatic transmission 20 or the hydraulic oil scooped up by the chain 18 is a first protrusion 112g extending along the side edge of the recess 112f. In addition, the second protrusion 112h extends along the upper edge of the recess 112f. Therefore, in the power transmission device 10, it becomes possible to collect more hydraulic oil in the recess 112f. Furthermore, by providing an opening 111o having a relatively large opening area at the upper part of the wall 111a of the front support 111, the oil 111 scattered with the rotation of the rotating element of the automatic transmission 20 is covered with the wall 111a and the cover member 112. More space 11x can be introduced. As a result, in the power transmission device 10, the oil that splashes with the rotation of the rotating element of the automatic transmission 20 and the oil that is scooped up by the chain 18 with the rotation of the drive sprocket 181 are used effectively. The bearing 147 can be lubricated extremely well.

  In addition, a first washer 100 is disposed between the support portion 112 b of the cover member 112 and the drive sprocket 181 in the axial direction, and radially outward from a part of the outer periphery of the ring portion 101 of the first washer 100. The extended extension portion 105 extends upward from the outer peripheral surface of the support portion 112b and faces the annular wall portion 112a through the recess 112f. As a result, the extension part 105 restricts the hydraulic oil collected in the recess 112f from flowing out from the end face side of the support part 112b on the drive sprocket 181 side, and more hydraulic oil flows into the oil hole 112c. It becomes possible to make it.

  Further, the support portion 112b of the cover member 112 has a retaining hole 112i extending in the axial direction so as to communicate with the oil hole 112c from the end surface on the drive sprocket 181 side. Further, the first washer 100 protrudes from the ring portion 101 in the axial direction, and the retaining protrusion is inserted into the retaining hole 112i of the cover member 112 so that the projecting portion 103b can be engaged with the inner peripheral surface of the oil hole 112c. Part 103. Thus, the retaining hole 112i formed in the support part 112b of the cover member 112, and the oil hole 112c for lubricating the radial bearing 147 disposed between the support part 112b and the sleeve 141 of the pump impeller 140, , It is not necessary to form a dedicated hole in the support portion 112b having an inner peripheral surface that engages with the retaining projection 103, and an increase in manufacturing cost of the power transmission device 10 can be suppressed. Become. Furthermore, the retaining protrusion 103 of the first washer 100 inserted into the retaining hole 112i is engaged with the inner peripheral surface of the oil hole 112c for lubricating the radial bearing 147, whereby the first washer 100 from the cover member 112 is engaged. Dropout is regulated. Therefore, the cover member 112 and the first washer 100 can be attached to the transmission case 11 at the same time, and the assemblability of the power transmission device 10 can be improved. As a result, it is possible to improve the assemblability of the power transmission device 10 while suppressing an increase in the manufacturing cost of the power transmission device 10.

  In addition, the cover member 112 has a detent hole 112j extending in the axial direction from the end surface on the drive member side of the support portion 112b at a position spaced from the retaining hole 112i in the circumferential direction. Further, the first washer 100 protrudes in the axial direction from the ring portion 101 at a position spaced apart from the retaining projection 103 in the circumferential direction, and is inserted into the detent hole 112j of the cover member 112. Have Accordingly, it is possible to restrict the rotation of the first washer 100 relative to the cover member 112 while preventing the first washer 100 from falling off the cover member 112.

  For example, when the radial bearing 147 is lubricated by the hydraulic fluid supplied from the starter 12 side, the oil hole 112c of the cover member 112 may be used for causing the hydraulic fluid that lubricated the radial bearing 147 to flow out. Good. The oil pump 17 of the power transmission device 10 has an external gear 171 connected to the sleeve 141 via a winding transmission mechanism including a chain 18, a drive sprocket 181, and a driven sprocket 182. 17 may be connected to the pump impeller 140 via a gear train including a drive gear that rotates integrally with the sleeve 141.

  As described above, the power transmission device according to the present invention is a power transmission device including a fluid transmission device having a pump impeller and a turbine runner, a transmission, and a case housing the fluid transmission device and the transmission. A cover member having an annular wall portion fixed to the case so as to be positioned between the fluid transmission device and the transmission, and a cylindrical portion extending in an axial direction from an inner periphery of the annular wall portion; Arranged in a gap between the inner peripheral surface of the cylindrical portion of the cover member and the outer peripheral surface of the sleeve extending in the axial direction from the pump impeller toward the transmission, the pump impeller is rotatable. A drive member connected to an oil pump which rotates integrally with the sleeve of the pump impeller and which is arranged on a shaft different from the input shaft of the transmission, and the cover A washer disposed between the cylindrical portion of the member and the drive member in the axial direction, and the cover member communicates with the gap in which the bearing is disposed. An oil hole penetrating the upper part of the portion, and a retaining hole extending in the axial direction so as to communicate with the oil hole from the end surface of the tubular portion on the drive member side, and the washer A ring portion that contacts the end surface; and a retaining projection that protrudes in the axial direction from the ring portion and is inserted into the retaining hole of the cover member so as to be engageable with the inner peripheral surface of the oil hole. It is characterized by that.

  The power transmission device includes a cover member having an annular wall portion fixed to the case so as to be positioned between the fluid transmission device and the transmission, and a cylindrical portion extending in an axial direction from the inner periphery of the annular wall portion. The bearing is disposed in a gap between the inner peripheral surface of the cylindrical portion of the cover member and the outer peripheral surface of the sleeve extending in the axial direction from the pump impeller toward the transmission, and rotatably supports the pump impeller. And a drive member that rotates integrally with a sleeve of the pump impeller and is connected to an oil pump that is disposed on a shaft different from the input shaft of the transmission, and a cylindrical portion of the cover member and the drive member in the axial direction. And a washer disposed between them. Further, the cover member has an oil hole that penetrates through the upper portion of the cylindrical portion of the cover member so as to communicate with a gap in which the bearing is disposed, and a shaft that communicates with the oil hole from the end surface on the drive member side of the cylindrical portion. And a retaining hole extending in the direction. Further, the washer is a retaining portion inserted into the retaining hole of the cover member so as to be able to engage with the inner peripheral surface of the oil hole while protruding from the ring portion in the axial direction while being in contact with the end surface of the cylindrical portion. And a protrusion. In this way, by connecting the retaining hole formed in the cylindrical part of the cover member and the oil hole through which the lubricating oil of the bearing arranged between the cylindrical part and the sleeve of the pump impeller flows, It is no longer necessary to form a dedicated hole in the cylindrical portion with an inner peripheral surface that engages with the retaining protrusion, and an increase in the manufacturing cost of the power transmission device can be suppressed. Further, the stopper protrusion of the washer inserted into the stopper hole engages with the inner peripheral surface of the oil hole, so that the washer is prevented from dropping from the cover member. Accordingly, the cover member and the washer can be attached to the case at the same time, and the assemblability of the power transmission device can be improved. As a result, it is possible to improve the assemblability of the power transmission device while suppressing an increase in manufacturing cost of the power transmission device.

  Further, the cover member may have a rotation-preventing hole extending in an axial direction from an end surface of the cylindrical portion on the driving member side at a position spaced from the retaining hole in the circumferential direction, and the washer You may have an at least 1 rotation prevention protrusion part which protrudes in the axial direction from the said ring part in the position spaced apart from the protrusion part in the circumferential direction, and is inserted in the said rotation prevention hole of the said cover member. Accordingly, it is possible to restrict the rotation of the washer relative to the cover member while preventing the washer from falling off the cover member.

  Furthermore, the cover member may have a recess formed in the annular wall portion so as to be recessed from the transmission side toward the fluid transmission device side above the oil hole, and the washer includes the ring It may have an extending portion extending radially outward from a part of the outer periphery of the portion, and the extending portion projects upward from the outer peripheral surface of the cylindrical portion and the annular shape via the recess You may attach to this cylindrical part so that a wall part may be opposed. As a result, the oil scooped up with the rotation of the drive member and the oil scattered with the rotation of the rotating element of the transmission are collected in the recess of the cover member and flowed down from the recess to the oil hole. Can be used for bearing lubrication. In addition, it is possible to restrict the oil collected in the concave portion from flowing out from the end face side of the cylindrical portion by the extending portion of the washer, so that more oil can flow into the oil hole.

  The drive member may be a drive sprocket coupled to the oil pump via a chain.

  And this invention is not limited to the said embodiment at all, and it cannot be overemphasized that a various change can be made within the range of the extension of this invention. Furthermore, the mode for carrying out the invention described above is merely a specific embodiment of the invention described in the column for solving the problem, and is described in the column for means for solving the problem. It is not intended to limit the elements of the invention.

  The present invention can be used in the manufacturing industry of clutches and transmissions.

  DESCRIPTION OF SYMBOLS 10 Power transmission device, 11 Transmission case, 11x space, 12 Starting device, 13 Front cover, 15 Lockup clutch, 16 Damper mechanism, 17 Oil pump, 18 Chain, 20 Automatic transmission, 20i Input shaft, 20m Intermediate shaft, 20o Output shaft, 21 first planetary gear, 21c first carrier, 21p first pinion gear, 21r first ring gear, 21s first sun gear, 22 second planetary gear, 22c second carrier, 22p second pinion gear, 22r second ring gear, 22s 2nd sun gear, 23c 3rd carrier, 23p 3rd pinion gear, 23r 3rd ring gear, 23s 3rd sun gear, 24p 4th pinion gear, 24s 4th sun gear, 25 Ravigneaux type planetary gear mechanism, 100 1st washer, 101 ring Part, 102 support part, 103 retaining projection part, 103a pin, 103b projection part, 104 detent projection part, 105 extension part, 110 case body, 111 front support, 111a wall part, 111b cylindrical part, 111o opening part, 112 cover member, 112a annular wall part, 112b support part, 112c oil collecting hole, 112d oil collecting hole, 112e communication hole, 112f recessed part, 112g first projecting part, 112h second projecting part, 112i retaining hole, 112j anti-rotation hole, 115 Center Support, 140 Pump Impeller, 140a Pump Shell, 140b Pump Blade, 141 Sleeve, 141a Flange, 141b Cylindrical Part, 141c Engaging Protrusion, 142 Turbine Runner, 143 Stator, 144 One Way Clutch, 145 Stator , 146 ring member, 147 radial bearing, 148 oil seal, 170 rotor, 171 external gear, 172 internal gear, 173 pump body, 174 pump cover, 181 drive sprocket, 182 driven sprocket, 200 second washer, 201 ring , 204 Anti-rotation protrusion, B1, B2 brake, C1, C2, C3, C4 clutch.

Claims (4)

In a power transmission device including a fluid transmission device having a pump impeller and a turbine runner, a transmission, and a case housing the fluid transmission device and the transmission,
A cover member having an annular wall portion fixed to the case so as to be positioned between the fluid transmission device and the transmission, and a cylindrical portion extending in an axial direction from an inner periphery of the annular wall portion;
Arranged in a gap between the inner peripheral surface of the cylindrical portion of the cover member and the outer peripheral surface of the sleeve extending in the axial direction from the pump impeller toward the transmission, the pump impeller is rotatable. Bearings to support
A drive member that rotates integrally with the sleeve of the pump impeller and is connected to an oil pump disposed on a shaft different from the input shaft of the transmission;
A washer disposed between the cylindrical portion of the cover member and the drive member in the axial direction;
The cover member includes an oil hole that passes through an upper portion of the cylindrical portion of the cover member so as to communicate with the gap in which the bearing is disposed, and the oil hole from an end surface of the cylindrical portion on the drive member side A retaining hole extending in the axial direction so as to communicate with the
The washer is provided in the retaining hole of the cover member so as to be able to engage with an inner peripheral surface of the oil hole while projecting in an axial direction from the ring portion contacting the end surface of the cylindrical portion. A power transmission device having a retaining protrusion to be inserted. The power transmission device according to claim 1,
The cover member has a rotation-preventing hole extending in the axial direction from an end surface on the drive member side of the tubular portion at a position spaced in the circumferential direction from the retaining hole,
The washer has at least one detent projection that protrudes in the axial direction from the ring portion at a position spaced circumferentially from the retaining projection and is inserted into the detent hole of the cover member. Power transmission device. In the power transmission device according to claim 1 or 2,
The cover member is
Having a recess formed in the annular wall so as to be recessed from the transmission side toward the fluid transmission device above the oil hole;
The washer has an extending portion extending radially outward from a part of the outer periphery of the ring portion, and the extending portion projects upward from the outer peripheral surface of the cylindrical portion, and passes through the recess. The power transmission device is attached to the cylindrical portion so as to face the annular wall portion. In the power transmission device according to any one of claims 1 to 3,
The drive member is a drive sprocket coupled to the oil pump via a chain.