WO2016129346A1

WO2016129346A1 - Power transmission device

Info

Publication number: WO2016129346A1
Application number: PCT/JP2016/051571
Authority: WO
Inventors: 佑介 ▲高▼▲橋▼; 宣和池; 昌士鬼頭
Original assignee: アイシン・エィ・ダブリュ株式会社
Priority date: 2015-02-13
Filing date: 2016-01-20
Publication date: 2016-08-18

Abstract

A first washer 100 is arranged between a support part 221b of a converter housing and a drive sprocket that rotates integrally with a pump impeller, and a pawl part 105 that protrudes in the axial direction and extends along the outer periphery of a ring part 101 is formed in the first washer 100 so as to be positioned further radially outward than is the drive sprocket. A second washer 200 is arranged between a wall part 223a and the drive sprocket so as to not rotate relative to a front support, and a hole 205 into which the pawl part 105 is fitted is formed in the second washer 200 so as to be positioned further radially outward than is the drive sprocket.

Description

Power transmission device

The present disclosure relates to a power transmission device including a fluid transmission device having a pump impeller and a turbine runner, a transmission, a housing that houses the fluid transmission device, and a case that houses the transmission and is fastened to the housing.

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, in order to support the disc spring between the first sprocket and the torque converter housing in the radial direction, the cylindrical portion that supports the inner peripheral surface of the disc spring is axially extended from the first sprocket. It is extended to. For this reason, since the first sprocket has an asymmetric structure on the front and back, there is a risk of erroneous assembly, and the conventional power transmission device still has room for improvement in terms of the assembly of the first sprocket. Moreover, when providing the cylindrical part which supports a disc spring in a 1st sprocket, it becomes necessary to ensure the intensity | strength of the said cylindrical part etc., it becomes difficult to reduce the size of a 1st sprocket, and a power transmission device is large sized. There is a risk of becoming. On the other hand, when the cylindrical portion supporting the disc spring is omitted from the first sprocket, the disc spring is temporarily fixed to the torque converter housing with, for example, grease, and then the cover on which the thrust bearing and the first sprocket are assembled is attached. The torque converter housing and the disc spring need to be assembled together. In this case, by temporarily fixing the disc spring to the torque converter housing, the manufacturing process is increased, and the disc spring is dropped from the torque converter housing when assembled to the cover, and the assemblability is impaired. There is also a risk.

Therefore, the invention of the present disclosure improves the assemblability of a power transmission device having a drive sprocket connected to an oil pump disposed on a shaft different from the input shaft of the transmission via a chain and suppresses an increase in size. The main purpose is to do.

A power transmission device of the present disclosure includes a fluid transmission device having a pump impeller and a turbine runner, a transmission, a housing that houses the fluid transmission device, and a case that houses the transmission and is fastened to the housing. A power transmission device including a support member having a wall portion fixed to the case so as to be positioned between the fluid transmission device and the transmission; and between the housing and the wall portion of the support member. A drive sprocket which is disposed and rotates integrally with the pump impeller and which is connected to an oil pump disposed on a shaft different from the input shaft of the transmission via a chain; and the housing and the drive sprocket A first washer disposed between the wall and the drive sprocket so as not to rotate with respect to the support member; A second washer disposed between each of the first and second washers, each including a ring portion that axially supports a corresponding surface of the drive sprocket, and one of the first and second washers. Is formed so that a claw portion that protrudes in the axial direction and extends along the outer periphery of the ring portion is positioned radially outward from the drive sprocket, and the other claw is provided on the other of the first and second washers. The hole into which the portion is fitted is formed so as to be located on the outer side in the radial direction than the drive sprocket.

In this manner, the claw portion extending along the outer periphery of the ring portion is formed so as to be positioned radially outward from the drive sprocket, and the hole portion into which the claw portion is fitted is radially outward from the drive sprocket. By forming so as to be positioned, the pair of claw portions and hole portions that are fitted to each other facilitates rotation of the first washer relative to the second washer and movement of the first washer relative to the second washer in the radial direction of the ring portion. It becomes possible to regulate. Further, if one of the claw portions of the first and second washers is fitted into the other hole portion, the rotation of the first washer relative to the support member can be restricted by the second washer. In addition, by arranging the first and second washers on both sides in the axial direction of the drive sprocket, it is not necessary to provide a support part for supporting the washer on the drive sprocket, and the drive sprocket has a symmetrical structure It becomes possible to do. In addition, since the first washer can be assembled to the support member by fitting one claw portion of the first and second washers into the other hole portion, the first washer is temporarily attached to the housing. It is not necessary to assemble both of them to the support member after stopping. As a result, the assembly of the first and second washers and the drive sprocket can be facilitated and the increase in size of these members can be suppressed, so that the assembly of the power transmission device can be improved and the increase in size can be suppressed. Is possible.

It is a schematic structure figure showing the power transmission device of this indication. It is an enlarged view which shows the winding transmission mechanism contained in the power transmission device of this indication. 2 is an operation table showing a relationship between each shift stage of an automatic transmission included in the power transmission device of FIG. 1 and operation states of clutches and brakes. It is a principal part expanded sectional view which shows the power transmission device of this indication. It is a top view showing the 1st washer contained in the power transmission device of this indication. It is a top view showing the 2nd washer contained in the power transmission device of this indication. It is sectional drawing which shows the 1st and 2nd washer. It is a top view which shows the other 1st washer applicable to the power transmission device of FIG. It is a top view which shows the 2nd washer which concerns on the deformation | transformation aspect applicable to the power transmission device of FIG. It is sectional drawing which shows the 1st and 2nd washer which concerns on the other deformation | transformation aspect applicable to the power transmission device of FIG.

Next, an embodiment for carrying out the invention of the present disclosure will be described with reference to the drawings.

FIG. 1 is a schematic configuration diagram illustrating a power transmission device 20 of the present disclosure. The power transmission device 20 shown in the figure is connected to a crankshaft of an engine (not shown) mounted on a front-wheel drive type vehicle and can transmit power from the engine to left and right drive wheels (front wheels) (not shown). is there. As shown in the figure, the power transmission device 20 includes a transmission case 22, a torque converter (starting device) 23, an oil pump 24, an automatic transmission 25 accommodated in the transmission case 22, a gear mechanism (gear train) 40, a differential. A gear (differential mechanism) 50 and the like are included.

The transmission case 22 is located between the converter housing 221 and the transaxle case 222 in addition to the converter housing 221 and the transaxle case 222 fastened (fixed) to the converter housing 221. A front support (support member) 223 that is fastened (fixed) to the front. In the present embodiment, the converter housing 221 and the transaxle case 222 are made of, for example, an aluminum alloy, and the front support 223 is made (cast) of a steel material (iron alloy).

The torque converter 23 is disposed inside the input-side pump impeller 23p connected to the crankshaft of the engine, the output-side turbine runner 23t, the pump impeller 23p, and the turbine runner 23t connected to the input shaft 26 of the automatic transmission 25. A stator 23s that is arranged to rectify the flow of hydraulic oil from the turbine runner 23t to the pump impeller 23p, a one-way clutch 23o that restricts the rotational direction of the stator 23s in one direction, a lock-up clutch 23c, a damper device 23d, and the like.

The oil pump 24 meshes with a pump assembly including a pump body and a pump cover, an external gear (inner rotor) connected to the pump impeller 23p of the torque converter 23 via the winding transmission mechanism 240, and the external gear. It is configured as a gear pump having an internal gear (outer rotor) or the like, and is arranged on a different shaft from the input shaft 26 of the automatic transmission 25. The oil pump 24 is driven by the power from the engine via the winding transmission mechanism 240, sucks hydraulic oil (ATF) stored in an oil pan (not shown), and pumps it to a hydraulic control device (not shown). As shown in FIG. 2, the winding transmission mechanism 240 includes a drive sprocket (first sprocket) 241 that rotates integrally with the pump impeller 23 p of the torque converter 23 and a driven sprocket that rotates integrally with the external gear of the oil pump 24. (Second sprocket) 242 and a chain 243 wound around the drive sprocket 241 and the driven sprocket 242.

The automatic transmission 25 is configured as an eight-speed transmission, and as shown in FIG. 1, a double pinion type first planetary gear mechanism 30, a Ravigneaux type second planetary gear mechanism 35, and an input 4 clutches C1, C2, C3 and C4, two brakes B1 and B2, and a one-way clutch F1 for changing the power transmission path from the side to the output side.

The first planetary gear mechanism 30 is engaged with a sun gear (fixed element) 31 that is an external gear and a ring gear 32 that is an internal gear arranged concentrically with the sun gear 31 and one of the gears is engaged with the sun gear 31. The other has a planetary carrier 34 that holds a plurality of pairs of two

pinion gears

33a and 33b meshing with the ring gear 32 so as to be rotatable (rotatable) and revolved. As shown in the figure, the sun gear 31 of the first planetary gear mechanism 30 is non-rotatably connected (fixed) to the transmission case 22 via the front support 223, and the planetary carrier 34 of the first planetary gear mechanism 30 is The input shaft 26 is connected so as to be integrally rotatable. The first planetary gear mechanism 30 is configured as a so-called reduction gear, and decelerates the power transmitted to the planetary carrier 34 as an input element and outputs it from a ring gear 32 as an output element.

The second planetary gear mechanism 35 includes a first sun gear 36a and a second sun gear 36b which are external gears, a ring gear 37 which is an internal gear disposed concentrically with the first and

second sun gears

36a and 36b, A plurality of short pinion gears 38a meshing with one sun gear 36a, a plurality of long pinion gears 38b meshing with the second sun gear 36b and the plurality of short pinion gears 38a and meshing with the ring gear 37, a plurality of short pinion gears 38a and a plurality of long pinion gears 38b And a planetary carrier 39 that holds the magnet so as to be rotatable (rotatable) and revolved. The ring gear 37 of the second planetary gear mechanism 35 functions as an output member of the automatic transmission 25, and the power transmitted from the input shaft 26 to the ring gear 37 is transmitted to the left and right via the gear mechanism 40, the differential gear 50 and the drive shaft 51. Is transmitted to the driving wheel. The planetary carrier 39 is supported by the transmission case 22 via the one-way clutch F1, and the rotation direction of the planetary carrier 39 is limited to one direction by the one-way clutch F1.

The clutch C1 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like. The ring gear 32 of the first planetary gear mechanism 30 and the second planetary gear mechanism 35 This is a multi-plate friction hydraulic clutch capable of connecting the first sun gear 36a to each other and releasing the connection therebetween. The clutch C2 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like. The input shaft 26 and the planetary carrier 39 of the second planetary gear mechanism 35 are connected to each other. It is a multi-plate friction type hydraulic clutch that can be connected and released from both. The clutch C3 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like. The ring gear 32 of the first planetary gear mechanism 30 and the second planetary gear mechanism 35 This is a multi-plate friction hydraulic clutch capable of connecting the second sun gear 36b to each other and releasing the connection therebetween. The clutch C4 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like. The planetary carrier 34 and the second planetary gear mechanism 35 of the first planetary gear mechanism 30 are provided. This is a multi-plate friction hydraulic clutch that can connect the second sun gear 36b to each other and release the connection therebetween.

The brake B1 has a hydraulic servo including a plurality of friction plates, separator plates, an oil chamber to which hydraulic oil is supplied, and the like, so that the second sun gear 36b of the second planetary gear mechanism 35 cannot be rotated to the transmission case 22. This is a multi-plate friction type hydraulic brake that can be fixed and can release the fixing of the second sun gear 36b to the transmission case 22. The brake B2 has a hydraulic servo including a plurality of friction plates, separator plates, an oil chamber to which hydraulic oil is supplied, and the planetary carrier 39 of the second planetary gear mechanism 35 is fixed to the transmission case 22 so as not to rotate. This is a multi-plate friction type hydraulic brake that can release the fixation of the planetary carrier 39 to the transmission case 22.

The one-way clutch F1 includes an inner race coupled to (fixed to) the planetary carrier 39 of the second planetary gear mechanism 35, an outer race, a plurality of sprags, a plurality of springs (plate springs), a cage, and the like. When the outer race rotates in one direction with respect to the race, torque is transmitted through each sprag, and when the outer race rotates in the other direction with respect to the inner race, both are rotated relative to each other. However, the one-way clutch F1 may have a configuration other than a sprag type such as a roller type.

These clutches C1 to C4 and brakes B1 and B2 operate by receiving and supplying hydraulic oil from a hydraulic control device (not shown). FIG. 3 shows an operation table showing the relationship between the respective speeds of the automatic transmission 25 and the operating states of the clutches C1 to C4, the brakes B1 and B2, and the one-way clutch F1. The automatic transmission 25 provides forward 1st to 8th speeds and reverse 1st and 2nd speeds by setting the clutches C1 to C4 and the brakes B1 and B2 to the states shown in the operation table of FIG. . Note that 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.

The gear mechanism 40 is fixed to a counter drive gear 41 connected to the ring gear 37 of the second planetary gear mechanism 35 of the automatic transmission 25 and a counter shaft 42 extending in parallel with the input shaft 26 of the automatic transmission 25. A counter driven gear 43 that meshes with the counter drive gear 41, a drive pinion gear 44 formed (or fixed) on the counter shaft 42, and a diff ring gear 45 that meshes with the drive pinion gear 44 and is connected to the differential gear 50.

Next, the structure around the converter housing 221 and the front support 223 in the power transmission device 20 will be described in detail with reference to FIGS. As shown in FIG. 4, the converter housing 221 constituting a part of the transmission case 22 includes an annular wall portion 221 a extending in the radial direction between the torque converter 23 and the automatic transmission 25 in the axial direction, and an annular wall. And a short cylindrical support portion 221b formed on the inner peripheral portion of the portion 221a.

The front support 223 constituting a part of the transmission case 22 is fastened (fixed) to the transaxle case 222 so as to be positioned between the annular wall portion 221a (torque converter 23) of the converter housing 221 and the automatic transmission 25. ) Wall portion 223a, a first tubular portion 223b extending in the axial direction from the wall portion 223a toward the torque converter 23, and a first tube from the wall portion 223a toward the automatic transmission 25. It has the 2nd cylindrical part 223c extended on the opposite side and the axial direction from the shape part 223b.

As shown in FIG. 4, the pump impeller 23p constituting the torque converter 23 has a sleeve 230 joined by welding to the inner peripheral portion of the pump shell that is tightly fixed to the front cover. The sleeve 230 is formed of a steel material (iron alloy) like the pump shell and the like, and an annular flange portion 230a joined to the inner peripheral portion of the pump shell, and automatic transmission from the inner peripheral portion of the flange portion 230a. And a cylindrical portion 230b extending in the axial direction of the input shaft 26 toward the machine 25 side (left side in FIG. 4). Further, the free end portion (left end portion in FIG. 4, end portion on the automatic transmission 25 side) of the cylindrical portion 230 b of the sleeve 230 is engaged with a boss portion of the drive sprocket 241 of the winding transmission mechanism 240. A plurality of (for example, two) protrusions 230c that are respectively fitted in the grooves are formed.

The first cylindrical portion 223b of the front support 223 is fitted (inserted) into the cylindrical portion 230b of the sleeve 230 from the automatic transmission 25 side (left side in FIG. 4). A radial bearing 90 is interposed between the outer peripheral surface of the cylindrical portion 230 b of the sleeve 230 and the support portion 221 b of the converter housing 221. Thus, the sleeve 230, that is, the pump impeller 23p, is rotatably supported by the converter housing 221 and the front support 223, that is, the transmission case 22.

As shown in FIG. 4, the upper portion of the support portion 221 b of the converter housing 221 has one piece extending obliquely so as to approach the flange portion 230 a of the sleeve 230 from the outer peripheral side to the inner peripheral side of the support portion 221 b. An oil hole 221c is formed. The oil hole 221c communicates with the oil collection hole 221d and the large diameter oil collection hole 221d that opens toward the wall portion 223a of the front support 223 on the outer peripheral surface of the support portion 221b and opens on the inner peripheral surface of the support portion 221b. And a communication hole 221e having a smaller diameter than the oil collecting hole 221d. Further, an oil seal 95 is interposed between the support portion 221 b of the converter housing 221 and the outer peripheral surface of the cylindrical portion 230 b of the sleeve 230 so as to be closer to the flange portion 230 a of the sleeve 230 than the radial bearing 90. . The communication hole 221e constituting the oil hole 221c opens between the radial bearing 90 and the oil seal 95 as shown in the figure.

Further, the inner race of the one-way clutch 23o of the torque converter 23 is spline-fitted with a hollow stator shaft 235 formed of steel (iron alloy), and the stator 23s is connected to the stator shaft via the one-way clutch 23o. 235. The stator shaft 235 is press-fitted (fitted) into the second cylindrical portion 223 c of the front support 223 so as to surround the input shaft 26. A serration (not shown) is formed on the inner peripheral surface of the free end portion (left end portion in FIG. 4) of the second cylindrical portion 223c, and the second cylindrical portion is formed on a part of the outer peripheral surface of the stator shaft 235. A serration (not shown) that meshes with the serration formed at the free end of 223c is formed. Thereby, the stator shaft 235 is fixed to the front support 223, that is, the transmission case 22 so as not to rotate. A bush (bearing) is interposed between the inner peripheral surface of the stator shaft 235 and the outer peripheral surface of the input shaft 26.

Further, between the outer peripheral surface of the stator shaft 235 and the inner peripheral surface of the cylindrical portion 230b of the sleeve 230, power is transmitted via hydraulic oil by the pump impeller 23p and the turbine runner 23t. An oil passage 23y communicating with the fluid transmission chamber 23x of the torque converter 23 is defined. Hydraulic fluid (circulation pressure) from a hydraulic control device (not shown) is supplied to the fluid transmission chamber 23x via an oil passage formed in the front support 223, an oil passage formed in the input shaft 26, an oil hole, and the like. The hydraulic fluid that has flowed through the fluid transmission chamber 23x is returned to the hydraulic control device via the oil passage 23y, the oil passage 223r formed in the wall portion 223a of the front support 223, and the like. Further, a seal mounting groove is formed on the outer peripheral surface of the first cylindrical portion 223b of the front support 223, and a seal member 99 such as a seal ring is disposed in the seal mounting groove. As a result, the hydraulic oil flowing out from the fluid transmission chamber 23x is discharged from the fluid transmission chamber 23x by the seal member 99 disposed between the outer peripheral surface of the first cylindrical portion 223b and the inner peripheral surface of the cylindrical portion 230b of the sleeve 230. Leakage to the front support 223 side through the gap between the portion 223b and the cylindrical portion 230b of the sleeve 230 can be restricted.

The drive sprocket 241 of the winding transmission mechanism 240 is rotatably supported by the first tubular portion 223b of the front support 223 so as to be positioned between the support portion 221b of the converter housing 221 and the wall portion 223a of the front support 223. Is done. And the protrusion part 230c of the sleeve 230 is engage | inserted by each engagement groove formed in the boss | hub part of the drive sprocket 241. FIG. As a result, the pump impeller 23p and the drive sprocket 241 are coupled so as to be integrally rotatable, and the external teeth of the oil pump 24 are driven by the power from the engine via the pump impeller 23p, the sleeve 230, the drive sprocket 241, the chain 243, and the driven sprocket 242. The gear and the internal gear can be rotationally driven. As shown in FIG. 4, the chain 243 is located between the annular wall portion 221 a of the converter housing 221 and the wall portion 223 a of the front support 223.

Further, the first washer 100 is disposed between the support portion 221b of the converter housing 221 and the drive sprocket 241 in the axial direction, and between the drive sprocket 241 and the wall portion 223a of the front support 223 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 FIGS. 5 and 7, the first washer 100 includes an annular ring portion 101, and the surface on the converter housing 221 side of the drive sprocket 241 is supported in the axial direction from one surface of the ring portion 101. An annular support portion 102 is extended. As shown in FIG. 5, a plurality of oil grooves 103 that allow the flow of hydraulic oil as a lubricating medium are formed on the surface of the support portion 102 at regular intervals in the circumferential direction. Further, the first washer 100 includes an overhanging portion 104 that protrudes radially outward from a part of the outer periphery of the ring portion 101, and a claw portion that protrudes from the surface of the overhanging portion 104 in the same direction and axial direction as the support portion 102. 105. As shown in FIG. 2, the overhanging portion 104 extends from the ring portion 101 so as to extend substantially in parallel with a straight line connecting the center of the drive sprocket 241 and the center of the driven sprocket 242 (see the one-dot chain line in FIG. 2). Is issued. The claw portion 105 is formed on the overhang portion 104 so as to be positioned radially outward from the outer periphery of the drive sprocket 241 and to extend in an arc shape along the outer periphery of the ring portion 101.

Further, the first washer 100 has an oil collecting portion 106 for receiving the oil scraped up by the chain 243 and guiding it to the oil hole 221c (oil collecting hole 221d) formed in the support portion 221b of the converter housing 221. . The oil collecting portion 106 extends from a part of the outer periphery of the ring portion 101 to the outside in the radial direction, and extends so as to protrude from the extending portion 107 toward the annular wall portion 221a of the converter housing 221. It is comprised by the taken out oil receiving part 108. FIG. The extension portion 107 extends from the ring portion 101 so as to extend vertically upward when the first washer 100 is disposed between the support portion 221b of the converter housing 221 and the drive sprocket 241. As shown in FIG. 2, the oil receiver 108 is formed in a left-right symmetrical and convex downward arc shape.

As shown in FIGS. 6 and 7, the second washer 200 includes an annular ring portion 201, and the surface on the front support 223 side of the drive sprocket 241 is supported in the axial direction from one surface of the ring portion 201. An annular support 202 is extended. As shown in FIG. 6, a plurality of oil grooves 203 that allow the flow of hydraulic oil as a lubricating medium are formed on the surface of the support portion 202 at regular intervals in the circumferential direction. In addition, the second washer 200 includes an overhanging portion 204 that protrudes radially outward from a part of the outer periphery of the ring portion 201, and an arcuate hole 205 formed in the overhanging portion 204.

As shown in FIG. 2, the overhanging portion 204 extends substantially in parallel with a straight line connecting the center of the drive sprocket 241 and the center of the driven sprocket 242 (see the alternate long and short dash line in FIG. 2) and extends the tension of the first washer 100. The ring portion 201 extends so as to face the protruding portion 104. Moreover, the overhang | projection part 204 is extended in the circumferential direction and radial direction rather than the overhang | projection part 104 of the 1st washer 100, as shown in FIG. The hole portion 205 is formed on the overhang portion 204 so as to be positioned radially outward from the outer periphery of the drive sprocket 241 and to extend in an arc shape along the outer periphery of the ring portion 201, so that the claw portion 105 of the first washer 100 It has a circumferential length slightly longer than the circumferential length and a radial length slightly longer than the thickness of the claw portion 105. Then, as shown in FIG. 7, the claw portion 105 of the first washer 100 is fitted into the hole portion 205 of the second washer 200.

Furthermore, the second washer 200 has a plurality (two in this embodiment) of protrusions 206 protruding from the surface of the ring part 201 opposite to the drive sprocket 241. As shown in FIG. 6, the plurality of protrusions 206 are arranged at unequal intervals along the circumferential direction of the ring portion 201. As shown in FIG. 4, the protrusions 206 are fitted in rotation-preventing holes 223 h formed at unequal intervals on the wall portion 223 a of the front support 223. Accordingly, the second washer 200 is disposed between the wall 223a and the drive sprocket 241 so as not to rotate with respect to the front support 223. When the first and

second washers

100, 200 are disposed between the converter housing 221 and the wall portion 223a of the front support 223, the claw portion 105 and the hole portion 205 have a drive sprocket as shown in FIG. It is surrounded by a chain 243 wound around 241 and a driven sprocket 242.

As described above, in the power transmission device 20, the first washer 100 is disposed between the support portion 221 b of the converter housing 221 and the drive sprocket 241, and the surface of the drive sprocket 241 on the converter housing 221 side is the first washer 100. The ring portion 101 is supported in the axial direction. Further, the second washer 200 is disposed between the wall portion 223a of the front support 223 and the drive sprocket 241 so as not to rotate with respect to the front support 223, and the surface of the drive sprocket 241 on the wall portion 223a side is The ring portion 201 of the second washer 200 is supported in the axial direction. Further, the first washer 100 has an overhanging portion 104 projecting radially outward from a part of the outer periphery of the ring portion 101, and an arc shape along the outer periphery of the ring portion 101 while projecting axially from the overhanging portion 104. And a claw portion 105 extending in the direction. The second washer 200 has an overhang portion 204 that projects radially outward from a part of the outer periphery of the ring portion 201, and an arc-shaped hole that is formed in the overhang portion 204 and into which the claw portion 105 is fitted. Part 205.

Thus, by forming the claw portion 105 and the hole portion 205 in an arc shape, the rotation of the first washer 100 with respect to the second washer 200 and the ring by the pair of claw portions 105 and the hole portion 205 fitted to each other. It becomes possible to regulate the movement of the first washer 100 with respect to the second washer 200 in the radial direction of the

portions

101 and 201 very well. Further, if the claw portion 105 of the first washer 100 is fitted into the hole 205 of the second washer 200, the rotation of the first washer 100 with respect to the front support 223 can be very well regulated by the second washer 200. .

Furthermore, by disposing the first and second washers 200 on both sides in the axial direction of the drive sprocket 241, it becomes unnecessary to provide a support portion for supporting the washer on the drive sprocket 241, and the drive sprocket 241 has a symmetric structure. It is possible to adopt what has. In addition, by fitting the claw portion 105 of the first washer 100 into the hole portion 205 of the second washer 200, the first washer 100 can be independently assembled to the front support 223, so that the converter housing 221 can be assembled. There is no need to assemble the first washer 100 to the front support 223 after temporarily fixing the first washer 100. As a result, the assembly of the first and

second washers

100, 200 and the drive sprocket 241 can be facilitated, and the increase in size of these members can be suppressed. Can be suppressed.

Further, the second washer 200 has a plurality of protrusions 206 protruding at unequal intervals along the circumferential direction from the surface of the ring portion 201 opposite to the drive sprocket 241, and each protrusion 206 is formed on the front support 223. The wall portions 223a are fitted in rotation stopper holes 223h formed at unequal intervals. As described above, the plurality of protrusions 206 of the second washer 200 and the rotation-preventing holes 223h of the wall portion 223a corresponding to the plurality of protrusions 206 are arranged at unequal intervals, whereby the second washer 200 with respect to the front support 223 is arranged. Since misassembly can be prevented, the assemblability of the power transmission device 20 can be further improved.

Furthermore, the first washer 100 has an oil collecting portion 106 that receives the hydraulic oil scraped up by the chain 243 and guides it to the oil hole 221 c of the converter housing 221. The hydraulic fluid guided from the oil collecting section 106 to the oil collecting hole 221d of the oil hole 221c is supplied as a lubrication cooling medium from the communication hole 221e to the radial bearing 90 that supports the sleeve 230 of the pump impeller 23p. Thereby, in the power transmission device 20, the seal member 99 is disposed between the first cylindrical portion 223b of the front support 223 and the inner peripheral surface of the sleeve 230 (cylindrical portion 230b) of the pump impeller 23p, and the fluid transmission chamber. It is possible to satisfactorily lubricate the radial bearing 90 that supports the sleeve 230 of the pump impeller 23p while satisfactorily suppressing the leakage of hydraulic oil from the 23x.

Further, the oil collecting portion 106 of the first washer 100 includes an extending portion 107 extending radially upward from a part of the outer periphery of the ring portion 101, and an annular wall portion of the converter housing 221 from the extending portion 107. The oil receiving portion 108 protrudes toward 221a and has a downwardly convex arc shape. As a result, the oil scraped up by the chain 243 by the oil collecting portion 106 of the first washer 100 can be well received and guided to the oil hole 221c of the converter housing 221.

FIG. 8 is a plan view showing a first washer 100B according to a modified embodiment applicable to the power transmission device 20, and FIG. 9 is a plan view showing a second washer 200B according to a modified embodiment applicable to the power transmission device 20. FIG. In addition, the same code | symbol is attached | subjected about the element same as the above-mentioned 1st and 2nd washer 100,200, and the overlapping description is abbreviate | omitted.

As shown in FIG. 8, in the first washer 100B, the oil collecting portion 106 (the extending portion 107 and the oil receiving portion 108) in the first washer 100 described above is omitted. That is, the oil collecting unit 106 may be omitted from the first washer 100 as long as the hydraulic oil scraped up by the chain 243 flows relatively smoothly into the oil hole 221c of the converter housing 221. As a result, the space occupied by the first washer 100B can be reduced and the first washer 100B can be made lighter.

Further, the overhanging portion 104B of the first washer 100B extends in the circumferential direction and the radial direction from the overhanging portion 104 of the first washer 100 described above, and the overhanging portion 104B includes the overhanging portion 104B as shown in FIG. Further, a hole 115 extending in an arc shape along the outer periphery of the ring portion 101 is formed so as to be positioned on the radially outer side than the outer periphery of the drive sprocket 241. Further, as shown in FIG. 9, a claw portion 215 extending in an arc shape along the outer periphery of the ring portion 201 is positioned on the outer side in the radial direction with respect to the outer periphery of the drive sprocket 241 in the protruding portion 204 </ b> B of the second washer 200 </ b> B. It is formed as follows. The claw portion 215 protrudes from the surface of the overhang portion 204B in the same direction as the support portion 202 and in the axial direction, and has a slightly shorter circumference than the circumference of the hole 115 of the first washer 100B, and the diameter of the hole 115. It has a thickness slightly shorter than the length in the direction. As shown in FIG. 10, the claw portion 215 of the second washer 200B is fitted into the hole portion 115 of the first washer 100B. Further, the claw portion 215 of the second washer 200B has a protruding portion 215x formed so as to protrude in the radial direction of the ring portion 201 on one end side (right end side in FIG. 9) from the central portion in the circumferential direction. Furthermore, the hole 115 of the first washer 100B includes a notch 115x that engages with the protrusion 215x.

Thus, the claw portion 215 is formed on the overhang portion 204B of the second washer 200B disposed between the wall portion 223a and the drive sprocket 241 so as not to rotate with respect to the front support 223, and the first washer 100B. A hole 115 may be formed in the overhanging portion 104B. Thus, after the second washer 200B is attached to the wall portion 223a of the front support 223 and the drive sprocket 241 is fitted into the first tubular portion 223b of the front support 223, the second washer is passed through the hole 115 of the first washer 100B. The claw portion 215 can be fitted into the hole portion 115 while viewing the claw portion 215 of the washer 200B. As a result, the assembly of the first washer 100B and thus the power transmission device 20 can be further improved.

Furthermore, since the claw 215 is fitted into the hole 115 so that the protrusion 215x and the notch 115x are engaged with each other, erroneous assembly of the first and

second washers

100, 200 can be prevented. As a result, the assemblability of the power transmission device 20 can be further improved. A protrusion similar to the protrusion 215x may be formed on the claw portion 105 of the first washer 100, and a notch similar to the notch 115x is formed in the hole 205 of the second washer 200 described above. May be. Further, the claw portion 105 of the first washer 100 and the claw portion 215 of the second washer 200B are formed so as to extend in an arc shape along the outer periphery of the

ring portion

101 or 201. However, the present invention is not limited to this. Absent. That is, the claw portion 105 and the claw portion 215 may be formed so as to extend linearly along the tangential direction of the outer periphery of the

ring portion

101 or 201, and the hole portion 205 and the hole portion 115 into which these are fitted are also included. You may form so that it may extend linearly.

As described above, the power transmission device according to the present disclosure includes the fluid transmission device (23) including the pump impeller (23p) and the turbine runner (23t), the transmission (25), and the fluid transmission device (23). In the power transmission device (20) including a housing (221) for housing and a case (222) for housing the transmission (25) and fastened to the housing (221), the fluid transmission device (23) A support member (223) having a wall portion (223a) fixed to the case (222) so as to be positioned between the transmission (25), the housing (221), and the support member (223); It is disposed between the wall portion (223a), rotates integrally with the pump impeller (23p), and inputs the transmission (25) via a chain (243). (26) A drive sprocket (241) connected to an oil pump (24) arranged on a different axis, and a first washer arranged between the housing (221) and the drive sprocket (241) (100, 100B) and a second washer (200, 200B) disposed between the wall (223a) and the drive sprocket (241) so as not to rotate with respect to the support member (223). The first and second washers (100, 100B, 200, 200B) each include a ring portion (101, 201) for axially supporting a corresponding surface of the drive sprocket (241). One of the second washers (100, 100B, 200, 200B) protrudes in the axial direction and has the ring portion (10 , 201) is formed so that the claw portions (105, 215) extending along the outer periphery of the drive sprocket (241) are positioned radially outward from the drive sprocket (241), and the first and second washers (100, 100B, 200). , 200B), the hole portions (205, 115) into which the claw portions (105, 215) are fitted are formed so as to be located radially outside of the drive sprocket (241). It is.

In this power transmission device, the first washer is disposed between the housing and the drive sprocket, and the housing side surface of the drive sprocket is supported in the axial direction by the ring portion of the first washer. Further, a second washer is disposed between the wall portion of the support member and the drive sprocket so as not to rotate with respect to the support member, and the surface of the drive sprocket on the support member side is formed by the ring portion of the second washer. Supported in the axial direction. Further, one of the first and second washers is formed with a claw portion that protrudes in the axial direction and extends along the outer periphery of the ring portion so as to be positioned radially outward from the drive sprocket. On the other side of the washer, a hole portion into which the claw portion is fitted is formed so as to be positioned on the radially outer side than the drive sprocket.

Further, the claw portions (105, 215) and the hole portions (205, 115) may each be formed in an arc shape. This makes it possible to very well regulate the rotation of the first washer relative to the second washer, the movement of the first washer relative to the second washer in the radial direction of the ring portion, and the rotation of the first washer relative to the support member.

Furthermore, each of the first and second washers (100B, 200B) may have an overhanging portion (104B, 204B) projecting radially outward from a part of the outer periphery of the ring portion (101, 201). The claw portion (215) may be formed in the overhang portion (204B) of the second washer (200B), and the hole portion (115) may be formed in the tension portion of the first washer (100B). You may form in a protrusion part (104B). As a result, after attaching the second washer to the wall portion of the support member and fitting the drive sprocket into the cylindrical portion of the support member, while visually observing the claw portion of the second washer through the hole portion of the first washer, Since the claw portion can be fitted into the hole portion, it is possible to further improve the assemblability of the first washer and the power transmission device.

Moreover, the said nail | claw part (215) may have the protrusion (215x) formed in the one end side rather than the center part in the circumferential direction, and the said hole (115) has the said protrusion (215x) and It may include a notch (115x) that engages. As a result, it is possible to prevent erroneous assembly of the first and second washers by fitting the claw into the hole so that the protrusion and the notch are engaged with each other. It is possible to further improve the performance.

Further, the second washer (200, 200B) has a plurality of protrusions (206) protruding at irregular intervals along the circumferential direction from the surface of the ring portion (201) opposite to the drive sprocket (241). The plurality of protrusions (206) may be fitted in rotation stopper holes (223h) formed at unequal intervals in the wall portion (223a) of the support member (223), respectively. Good. In this manner, by arranging the plurality of protrusions of the second washer and the non-rotating holes in the wall corresponding to the plurality of protrusions at unequal intervals, erroneous assembly of the second washer to the support member can be prevented. Since it can do, it becomes possible to improve the assembly property of a power transmission device further.

The first and second washers (100, 100B, 200, 200B) have the claw portions (105, 215) and the hole portions (205, 115), the drive sprocket (241) and the oil pump (24 ) Between the housing (221) and the wall (223a) of the support member (223) so as to be surrounded by a chain (243) wound around a driven sprocket (242) connected to May be.

Further, the support member (223) extends in the axial direction from the wall (223a) toward the fluid transmission device (23) and from the pump impeller (23p) toward the transmission (25). An outer peripheral surface of the sleeve (230) of the housing (221) and the pump impeller (23p) may have a cylindrical portion (223b) inserted into the sleeve (230) extended in the axial direction. A bearing (90) may be disposed between the cylindrical portion (223b) of the support member (223) and the inner peripheral surface of the sleeve (230) of the pump impeller (23p). In addition, a seal member (95) may be disposed, and the housing (221) may have an oil hole (221c) for supplying lubricating oil to the bearing (90). First washer (10 ) Is disposed between the housing (221) and the drive sprocket (241) and receives oil scooped up by the chain (243) to receive the oil hole (221c) of the housing (221). It may have an oil collecting part (106) led to. As a result, it is possible to satisfactorily lubricate the bearing that supports the sleeve of the pump impeller while satisfactorily suppressing leakage of hydraulic oil from the fluid transmission device.

The oil collecting part (106) includes an extending part (107) extending radially upward from a part of an outer periphery of the ring part (101) of the first washer (100), and the extending part. An oil receiving portion (108) that protrudes from the portion (107) toward the housing (221) and is formed in a downwardly convex arc shape may be included. As a result, the oil scooped up by the chain by the oil collecting portion of the first washer can be well received and guided to the oil hole of the housing.

And the invention of this indication is not limited to the said embodiment at all, and it cannot be overemphasized that various changes can be made within the range of the extension of this indication. Furthermore, the mode for carrying out the invention described above is merely a specific form of the invention described in the Summary of Invention column, and does not limit the elements of the invention described in the Summary of Invention column. Absent.

The invention of the present disclosure can be used in the power transmission device manufacturing industry and the like.

Claims

In a power transmission device including a fluid transmission device having a pump impeller and a turbine runner, a transmission, a housing that houses the fluid transmission device, and a case that houses the transmission and is fastened to the housing.
A support member having a wall portion fixed to the case so as to be positioned between the fluid transmission device and the transmission;
It is arranged between the housing and the wall of the support member, rotates together with the pump impeller, and is connected to an oil pump arranged on a shaft different from the input shaft of the transmission via a chain. Drive sprocket
A first washer disposed between the housing and the drive sprocket;
A second washer disposed between the wall portion and the drive sprocket so as not to rotate with respect to the support member;
Each of the first and second washers includes a ring portion that axially supports a corresponding surface of the drive sprocket,
One of the first and second washers is formed so that a claw portion that protrudes in the axial direction and extends along the outer periphery of the ring portion is positioned radially outward from the drive sprocket. The power transmission device, wherein the second washer is formed such that a hole portion into which the claw portion is fitted is positioned radially outside of the drive sprocket.
2. The power transmission device according to claim 1, wherein the claw portion and the hole are each formed in an arc shape.
In the power transmission device according to claim 1 or 2,
The first and second washers each have an overhanging portion protruding radially outward from a part of the outer periphery of the ring portion,
The claw portion is formed in the overhang portion of the second washer, and the hole portion is formed in the overhang portion of the first washer.
In the power transmission device according to any one of claims 1 to 3,
The claw portion has a protrusion formed on one end side with respect to the central portion in the circumferential direction, and the hole portion includes a cutout portion that engages with the protrusion.
In the power transmission device according to any one of claims 1 to 4,
The second washer has a plurality of protrusions protruding at unequal intervals along the circumferential direction from the surface of the ring portion opposite to the drive sprocket.
The plurality of protrusions are power transmission devices that are respectively fitted into rotation stop holes formed at unequal intervals on the wall portion of the support member.
In the power transmission device according to any one of claims 1 to 5,
The first and second washers are configured so that the claw portion and the hole portion are surrounded by a chain wound around the drive sprocket and a driven sprocket connected to the oil pump. A power transmission device disposed between the wall portions.
The power transmission device according to claim 6,
The support member includes a cylindrical portion that is inserted into a sleeve that extends in the axial direction from the wall portion toward the fluid transmission device and extends in the axial direction from the pump impeller toward the transmission. Have
Between the housing and the outer peripheral surface of the sleeve of the pump impeller, a bearing is disposed,
Between the cylindrical portion of the support member and the inner peripheral surface of the sleeve of the pump impeller, a seal member is disposed,
The housing has an oil hole for supplying lubricating oil to the bearing,
The first washer is disposed between the housing and the drive sprocket, and has an oil collecting portion that receives oil scooped up by the chain and guides it to the oil hole of the housing.
The power transmission device according to claim 7,
The oil collecting portion includes an extending portion that extends radially upward from a part of the outer periphery of the ring portion of the first washer, and protrudes from the extending portion toward the housing and protrudes downward. A power transmission device having an oil receiving portion formed in an arc shape.