JP2010249244A - Belt type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To suppress deterioration of circularity of the raceway surface of a bearing outer ring in a belt type continuously variable transmission. <P>SOLUTION: In the belt type continuously variable transmission configured so that a bearing outer ring 272, 284 for a pulley shaft 62, 64 is stored in a recessed part formed in a case, and the bearing outer ring 272, 284 is pressed from the outside of the recessed part by use of a retainer 280, 288 fixed to the case to be axially positioned and fixed, the retainer contact surface 304, 306 of the bearing outer ring 272, 284 is formed as an inclined surface such that the distance to a line 308, 310 orthogonal to the pulley shaft 62, 64 and passing through the center of a bearing 68, 72 is gradually increased with distance from the pulley shaft 62, 64, and the bearing outer ring pressing part 324, 326 of the retainer 280, 288 is formed to have a protruding part protruding toward the retainer contact surface 304, 306 of the bearing outer ring 272, 284. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention accommodates a pulley outer bearing ring for a pulley shaft in a recess formed in a case, and uses a retainer fixed to the case to press the bearing outer ring from the outside of the recess to position and fix it in the axial direction. The present invention relates to a continuously variable transmission (CVT).

  For example, Patent Document 1 proposes a pulley support structure for a belt-type continuously variable transmission that can prevent the occurrence of unnecessary backlash of a bearing that supports a pulley shaft.

  In the pulley support structure for a belt-type continuously variable transmission described in Patent Document 1, an inner ring of a bearing that rotatably supports a driven shaft that is a shaft of a pulley is coaxially fixed to the outer periphery of the driven shaft. Further, the outer ring of the bearing abuts one side surface on the case and a retainer abuts on the other side surface, and the outer ring is fixed to the case via the retainer. The retainer is an annular steel member, and its case-side contact portion becomes thinner toward the outer periphery in the radial direction, that is, the case-side contact surface moves away from the case toward the outer periphery in the radial direction. The slope is attached.

  Further, Patent Document 2 proposes a continuously variable transmission in which pulleys can be easily assembled and fixed.

  In the continuously variable transmission described in Patent Document 2, a pulley groove width variable primary pulley mounted on a primary shaft and a pulley groove width variable metal belt is mounted between the secondary shaft and the primary pulley. A secondary pulley. The bearing attached to the primary shaft is fixed in the case housing using a retainer. The retainer is fixed to the case housing by a bolt. A cover having a space portion that forms a bolt chamber for accommodating the bolt in a sealed state is attached to the case housing. A communication oil passage is formed in the cover, and the space portion and the communication oil passage are sealed with a gasket.

  Further, in Patent Document 3, a drive-side cylinder that forms a part of the drive-side hydraulic chamber can be positioned and fixed to the primary shaft by a retainer that supports the primary shaft of the drive pulley of the continuously variable transmission. A technology has been proposed that can firmly support and fix the frame.

  In the shaft support structure of a continuously variable transmission described in Patent Document 3, a torque converter and a forward / reverse switching unit are disposed on the drive pulley side in a transmission case having a main case and a side case, and the driven In a continuously variable transmission having an output clutch disposed on the pulley side, a primary shaft of the drive pulley is pivotally supported between the main case and the side case, and a cylinder that forms a part of the drive side hydraulic chamber of the drive pulley is provided. While being fixed to a primary shaft, it is set as the structure fixed and supported via the retainer which supports a primary shaft.

  Furthermore, Patent Document 4 proposes a technique that prevents rattling of the driven pulley, stabilizes the gear ratio of the continuously variable transmission, and improves the assembling property of the stopper plate.

  In the bearing structure of the continuously variable transmission described in Patent Document 4, a bearing holding hole is provided in the transmission case, a contact surface is provided in the bearing holding hole, a guide hole is provided in the transmission case, and the driven-side bearing is provided. A stopper plate for fixing is provided. The inner ring is press-fitted and fixed with a bearing fixing nut, the outer ring of the driven bearing is press-fitted into the bearing holding hole, the outer surface of the outer ring is brought into contact with the contact surface, and the plate fixing bolt is inserted into the guide hole. While the stopper plate is in contact with the inner surface of the outer ring, a plate fixing nut is screwed onto a plate fixing bolt protruding from the transmission case to fix the driven bearing.

Japanese Patent No. 3315886 JP-A-11-153213 JP 2000-220709 A JP 2000-220710 A

  In general belt-type continuously variable transmissions, the outer ring of the bearing that supports the primary shaft on the transaxle rear cover side and the bearing that supports the secondary shaft on the transaxle rear cover side is accommodated in a recess formed in the case. is doing.

  Then, as shown in FIG. 6, a retainer 1000 fixed to the case is used to press and fix one end portion of the bearing outer ring 1002 from the outside of the concave portion in the axial direction.

  With respect to the contact between the retainer 1000 and the bearing outer ring 1002, the rigidity between the bolt fastening portion 1004 and the bearing outer ring pressing portion 1006 of the retainer 1000 is lowered to prevent strong contact. Thereby, the deformation of the bearing outer ring 1002 is suppressed, and the life and efficiency are improved.

  However, in the bearing race structure of the continuously variable transmission shown in FIG. 6, the preload for restraining the bearing is insufficient, and the elimination of one-sided contact (deterioration of roundness) is insufficient.

  If the rigidity between the bolt fastening part 1004 and the bearing outer ring pressing part 1006 is lowered, the deformation (tilt) of the bolt fastening part 1004 increases when the bolt 1008 is fastened. If it does so, the volt | bolt 1008 will incline with respect to the volt | bolt hole of the volt | bolt fastening part 1004, the frictional force of a screw surface will become large, a fastening force will become small, and preload will run short.

  Here, if the fastening torque of the bolt 1008 is increased in order to ensure the preload, the contact between the retainer 1000 and the bearing outer ring 1002 becomes stronger.

  In the above countermeasure, the load direction of the retainer 1000 to the bearing outer ring 1002 is the anti-plate surface direction (toward the axial center direction), and deterioration of the roundness of the bearing outer ring 1002 is inevitable.

  In other words, the purpose of use of the retainer 1000 is to prevent axial misalignment of the shaft and to suppress belt misalignment. Therefore, in the secondary shaft, it is necessary to fasten the retainer 1000 with an axial force more than the reduction gear reaction force added to the shaft oil passage internal pressure. Therefore, in the primary shaft and the secondary shaft of the continuously variable transmission, the retainer 1000 that fixes the bearing outer ring 1002 to suppress the belt misalignment is bent because the retainer 1000 is floated and bolted, and FIG. 6, a load in an inner diameter oblique direction is applied to the bearing outer ring 1002. As a result, as shown by a broken line in FIG. 6, the roundness of the raceway surface of the bearing outer ring 1002 deteriorates and affects the bearing life, so that the rigidity of the retainer 1000 is increased in order to suppress bending, or It is necessary to take measures such as increasing the bearing size.

  The present invention has been made in view of the above technical problem, and an object of the present invention is to provide a belt type continuously variable transmission that can suppress the deterioration of the roundness of the raceway surface of the bearing outer ring.

  In order to achieve the above object, the present inventors may make the retainer contact surface of the bearing outer ring inclined to the inner diameter side, and the load direction of the retainer on the bearing outer ring may be inclined to the outer diameter side. Inspired.

  The specific invention based on this idea is as follows.

  The belt type continuously variable transmission according to the present invention accommodates a bearing outer ring for a pulley shaft in a recess formed in a case, and presses the bearing outer ring from the outside of the recess using a retainer fixed to the case in the axial direction. The belt-type continuously variable transmission is positioned and fixed to the retainer contact surface of the outer ring of the bearing, and the distance from the line passing through the bearing center is gradually increased as the distance from the pulley shaft increases. The bearing outer ring pressing portion of the retainer has a convex portion protruding toward the retainer contact surface of the bearing outer ring.

  In the above configuration, the retainer contact surface of the bearing outer ring is an inclined surface that is perpendicular to the pulley shaft and gradually increases in distance to the line passing through the bearing center as the distance from the pulley shaft increases, and the bearing outer ring pressing portion of the retainer is a bearing. Since it has the shape which has the convex part which protrudes toward the retainer contact surface of an outer ring | wheel, the load direction to the bearing outer ring | wheel of a retainer turns into an outer diameter side diagonal direction. Therefore, it is possible to suppress the deterioration of the roundness of the raceway surface of the bearing outer ring.

  According to the present invention, it is possible to provide a belt type continuously variable transmission that can suppress the deterioration of the roundness of the raceway surface of the bearing outer ring.

1 is a skeleton diagram of a transaxle when a belt type continuously variable transmission according to an embodiment of the present invention is applied to an FF vehicle (front-wheel drive vehicle with an engine in front). It is an expanded sectional view near the primary pulley and secondary pulley of the belt type continuously variable transmission. It is a figure which simplifies and shows the bearing race structure of the same belt type continuously variable transmission. It is a figure which simplifies and shows the bearing race structure of the belt type continuously variable transmission which concerns on the modification 1. FIG. It is a figure which simplifies and shows the bearing race structure of the belt type continuously variable transmission which concerns on the modification 2. FIG. It is a figure which simplifies and shows the bearing race structure of the conventional belt-type continuously variable transmission.

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

   FIG. 1 is a skeleton diagram of a transaxle when a belt type continuously variable transmission according to an embodiment of the present invention is applied to an FF vehicle.

 In FIG. 1, reference numeral 10 is an engine as a vehicle driving force source, and the type thereof is not particularly limited, but in the following description, a case where a gasoline engine is used as the engine 10 will be described for convenience.

  A transaxle 12 is provided on the output side of the engine 10, and this transaxle 12 is attached to a transaxle housing 14 attached to the rear end side of the engine 10 and an opening end opposite to the engine 10. A transaxle case 16 and a transaxle rear cover 18 attached to an opening end opposite to the transaxle housing 14 are sequentially provided.

  A torque converter 20 is provided inside the transaxle housing 14. Inside the transaxle case 16 and the transaxle rear cover 18, a forward / reverse switching mechanism 22, a belt type continuously variable transmission 24, and a final reduction gear 26 are provided. Is provided.

  An input shaft 30 coaxial with the crankshaft 28 is provided inside the transaxle housing 14, and a turbine runner 32 is attached to an end of the input shaft 30 on the engine 10 side. On the other hand, a front cover 36 is connected to the rear end of the crankshaft 28 via a drive plate 34, and a pump impeller 38 is connected to the front cover 36. The turbine runner 32 and the pump impeller 38 are disposed to face each other, and a stator 40 is provided inside the turbine runner 32 and the pump impeller 38.

  An oil pump 42 is provided between the torque converter 20 and the forward / reverse switching mechanism 22.

  The forward / reverse switching mechanism 22 is provided in a power transmission path between the input shaft 30 and the belt type continuously variable transmission 24. The forward / reverse switching mechanism 22 has a double pinion planetary gear mechanism 46. The planetary gear mechanism 46 includes a sun gear 48 provided on the input shaft 30, a ring gear 50 disposed concentrically with the sun gear 48 on the outer peripheral side of the sun gear 48, a pinion gear 52 meshed with the sun gear 48, a pinion gear 52, A pinion gear 54 meshed with the ring gear 50, and a carrier 56 that holds the pinion gears 52, 54 so as to be capable of rotating, and holds the pinion gears 52, 54 in an integrally revolving state around the sun gear 48. The carrier 56 and a primary shaft 62 (described later) of the belt type continuously variable transmission 24 are connected.

  Further, the forward / reverse switching mechanism 22 is provided with a forward clutch 58 for connecting / disconnecting the power transmission path between the carrier 56 and the input shaft 30 and a reverse brake 60 for controlling the rotation / fixation of the ring gear 50. Yes.

  The belt type continuously variable transmission 24 includes a primary shaft 62 disposed concentrically with the input shaft 30 and a secondary shaft 64 disposed parallel to the primary shaft 62. The primary shaft 62 is rotatably held by bearings 66 and 68, and the secondary shaft 64 is rotatably held by bearings 70 and 72, respectively.

  A primary pulley 74 is provided on the primary shaft 62 side, and a secondary pulley 76 is provided on the secondary shaft 64 side. The primary pulley 74 has a fixed sheave 78 formed integrally with the primary shaft 62 and a movable sheave 80 configured to be movable in the axial direction of the primary shaft 62. A V-shaped groove 82 is formed between the opposed surfaces of the fixed sheave 78 and the movable sheave 80.

  The belt-type continuously variable transmission 24 is provided with a hydraulic actuator 84 that moves the movable sheave 80 in the axial direction of the primary shaft 62 to move the movable sheave 80 and the fixed sheave 78 closer to or away from each other.

  On the other hand, the secondary pulley 76 similarly includes a fixed sheave 86 formed integrally with the secondary shaft 64 and a movable sheave 88 configured to be movable in the axial direction of the secondary shaft 64. A V-shaped groove 90 is formed between the surfaces facing the movable sheave 88.

  The belt-type continuously variable transmission 24 is provided with a hydraulic actuator 92 that moves the movable sheave 88 in the axial direction of the secondary shaft 64 to move the movable sheave 88 and the fixed sheave 86 closer to or away from each other.

  A belt 94 is wound around the groove 82 of the primary pulley 74 and the groove 90 of the secondary pulley 76. The belt 94 includes a large number of metal pieces and a plurality of steel rings. A counter driven gear 96 is fixed to the secondary shaft 64 and is held by bearings 98 and 100. The bearing 72 is provided on the transaxle rear cover 18 side, and a parking gear 102 is provided between the bearing 72 and the secondary pulley 76.

  An intermediate shaft 104 parallel to the secondary shaft 64 is supported by bearings 128 and 130 in a power transmission path between the counter driven gear 96 and the final reduction gear 26 of the belt type continuously variable transmission 24. The intermediate shaft 104 is provided with a counter driven gear 106 that meshes with the counter drive gear 96 and a final drive gear 108.

  The final reduction gear 26 has a hollow differential case 114 rotatably held by bearings 110 and 112, and a ring gear 116 that meshes with the final drive gear 108 is provided on the outer periphery of the differential case 114. Inside the differential case 114, a pinion shaft 120 to which two pinion gears 118 are attached is disposed. Two pinion gears 122 are meshed with the pinion gear 120 and communicated with the wheels 126 via the left and right drive shafts 124, respectively.

  Here, regarding the belt-type continuously variable transmission 24 described above, FIG. 2 is an enlarged sectional view of the vicinity of the primary pulley 74 and the secondary pulley 76 of the belt-type continuously variable transmission 24.

  The primary pulley 74 is arranged on the outer periphery of the primary shaft 62 (see FIG. 1) between a bearing 68 attached to the transaxle rear cover 18 and a bearing 66 attached to the transaxle case 16 side. The primary shaft 62 is rotatable about the axis 200, and two oil passages 202 and 204 are formed in the primary shaft 62 in the axial direction. The oil passages 202 and 204 are communicated with a hydraulic circuit of the hydraulic control device. The primary shaft 62 is provided with oil passages 206 and 208 that extend in the radial direction toward the outer peripheral surface thereof and communicate with the oil passage 202. The oil passage 206 and the oil passage 208 are provided at different positions in the axial direction. Specifically, the oil passage 206 is disposed closer to the bearing 68 than the oil passage 208.

  Further, the primary pulley 74 is provided with an oil passage 210 that extends in the radial direction toward the outer peripheral surface of the primary shaft 62 and communicates with the oil passage 204. The oil passage 210 is opened between the movable sheave 80 and the fixed sheave 78 and supplies oil for lubricating the belt 94 (see FIG. 1).

  On the other hand, a step 212 is formed between the opening of the oil passage 206 on the outer periphery of the primary shaft 62 and the bearing 68 so as to face the bearing 68.

  The movable sheave 80 includes an inner cylindrical portion 214 that slides along the outer peripheral surface of the primary shaft 62, a radial direction portion 216 that is continuous from the end on the fixed sheave 78 side of the inner cylindrical portion 214 toward the outer peripheral side, It has an outer cylinder portion 218 that is continuous with the outer peripheral end of the direction portion 216 and extends in the axial direction toward the bearing 68 side. An oil passage 220 penetrating from the inner peripheral surface to the outer peripheral surface is formed in the inner cylindrical portion 214. The oil passage 220 and the oil passage 208 communicate with each other via an annular notch 222 formed on the outer peripheral surface of the primary shaft 62.

  A partition wall 224 is disposed between the movable sheave 80 and the bearing 68. The partition wall 224 includes a radial portion 226 that forms the inner peripheral side of the partition wall 224, and a cylindrical portion 228 that is continuous with the outer peripheral end of the radial direction portion 226 and extends toward the radial direction portion 216 side of the movable sheave 80. The cylindrical portion 228 includes a radial portion 230 that is continuous with the end portion of the movable sheave 80 on the radial direction portion 216 side and extends outward. The radial portion 226 of the partition wall 224 is disposed between the step portion 212 and the bearing 68. A resin-made seal ring 232 is attached to the outer peripheral end of the radial direction portion 230 of the partition wall 224, and the seal ring 232 and the inner peripheral surface of the outer cylindrical portion 218 of the movable sheave 80 are relatively moved in the axial direction. Contact is possible, and a seal surface is formed at the contact portion.

  In this manner, the first hydraulic chamber 234 is formed in the space surrounded by the movable sheave 80 and the partition wall 224. The first hydraulic chamber 234 and the oil passage 220 are communicated with each other.

  Further, an axial groove 236 is formed on the inner peripheral surface of the inner cylindrical portion 214 of the movable sheave 80, and an axial groove 238 is formed on the outer peripheral surface of the primary shaft 62. A plurality of grooves 236 and 238 are formed at predetermined intervals in the circumferential direction. The primary shaft 62 and the movable sheave 80 are positioned so that each groove 236 and each groove 238 have the same phase in the circumferential direction, and a plurality of balls 240 straddling both the groove 236 and the groove 238 are disposed. Yes. The primary shaft 62 and the movable sheave 80 can be smoothly moved relative to each other in the axial direction by the grooves 236 and 238 and the ball 240, but the primary shaft 62 and the movable sheave 80 cannot be relatively moved in the circumferential direction. It is supposed to be in a state.

  Furthermore, an annular cylinder member 242 is attached to the outer periphery of the primary shaft 62. The cylinder member 242 includes a radial portion 244 and a cylindrical portion 246 that is continuous with the outer peripheral side of the radial direction portion 244 and extends in the axial direction toward the fixed sheave 78 side. The inner diameter of the cylindrical portion 246 is set larger than the outer diameter of the outer cylindrical portion 218 of the movable sheave 80.

  The inner peripheral portion of the radial portion 244 of the cylinder member 242 is disposed between the bearing 68 and the radial portion 226 of the partition wall 224.

  A nut 248 is fastened and fixed to the outer periphery of the primary shaft 62, and the bearing 68, the cylinder member 242, and the partition wall 224 are sandwiched in the axial direction of the primary shaft 62 by the nut 248 and the step portion 212. It is fixed to the position.

  The piston 250 is between the cylindrical portion 228 of the partition wall 224 and the cylindrical portion 246 of the cylinder member 242, and between the radial direction portion 244 of the cylinder member 242 and the outer cylindrical portion 218 of the movable sheave 80. Is provided. The piston 250 has a substantially disk shape, and an O-ring 252 made of a rubber-like elastic material is attached to the inner periphery of the piston 250, and a resin seal ring 254 is attached to the outer periphery of the piston 250. It is attached. The piston 250 is configured to be movable in the axial direction with respect to the partition wall 224 and the cylinder member 242. The O-ring 252 contacts the outer peripheral surface of the cylindrical portion 228 of the partition wall 224 to form a seal surface, and the seal ring 254 is formed. A seal surface is formed in contact with the inner peripheral surface of the cylindrical portion 246 of the cylinder member 242. A cylindrical sleeve 256 extending in the axial direction toward the bearing 68 is formed at the inner peripheral end of the piston 250.

  In this way, the second hydraulic chamber 258 is formed in the annular space surrounded by the cylinder member 242, the partition wall 224, and the piston 250.

  In addition, an oil passage 260 penetrating the partition wall 224 in the thickness direction is formed at a boundary portion between the radial portion 226 and the cylindrical portion 228 of the partition wall 224, and the first hydraulic chamber 234 and the second hydraulic pressure are formed. The chamber 258 communicates with the oil passage 260. An air chamber 262 is formed in a space surrounded by the partition wall 224, the piston 250, and the outer cylindrical portion 218 of the movable sheave 80, and an air passage 264 that communicates the air chamber 262 and the outside of the cylinder member 242 is provided. Yes.

  On the other hand, the secondary pulley 76 is disposed between the bearing 70 (not shown in FIG. 2) and the bearing 72 on the outer periphery of the secondary shaft 64 (see FIG. 1). The secondary shaft 64 can rotate around the axis 266, and an oil passage 268 is formed in the secondary shaft 64 in the axial direction. The oil passage 268 communicates with a hydraulic circuit of the hydraulic control device. An oil passage (not shown) extending in the radial direction toward the outer peripheral surface of the secondary shaft 64 and communicating with the oil passage 268 is provided. The oil passage includes the movable sheave 88 and the fixed sheave 86. Is communicated with the above-described hydraulic actuator 92 (see FIG. 1). A parking gear 102 is provided between the bearing 72 and the fixed sheave 86 of the secondary pulley 76 and is sandwiched by a nut 270 that is fastened and fixed to the outer periphery of the secondary shaft 64.

  The primary pulley 74 and the secondary pulley 76 configured as described above are attached to the transaxle rear cover 18 through a bearing 68 and a bearing 72, respectively, as will be described in detail below.

  In the primary pulley 74, the outer ring 272 of the bearing 68 for the primary shaft 62 is accommodated in a recess 274 formed in the transaxle rear cover 18 as a case, and the retainer 280 fixed to the transaxle rear cover 18 with a bolt 276A. Is used to press the one end of the bearing outer ring 272 toward the shim 282 mounted on the bottom of the recess 274 from the outside of the recess 274 (inside of the case).

  On the other hand, in the secondary pulley 76, the outer ring 284 of the bearing 72 for the secondary shaft 64 is housed in a recess 286 formed in the transaxle rear cover 18 as a case, and is fixed to the transaxle rear cover 18 with a bolt 276B. The retainer 288 is used to press and fix one end portion of the bearing outer ring 284 from the outside of the concave portion 286 toward the bottom portion of the concave portion 286 so as to be positioned and fixed in the axial direction.

  FIG. 3 is a diagram showing the bearing race structure of the belt type continuously variable transmission 24 in a simplified manner.

  Referring to FIG. 3, the bearings 68 and 72 for the shafts 62 and 64 are ball bearings using balls 300 and 302 as rolling elements, and the retainer contact surfaces 304 of the bearing outer rings 272 and 284, respectively. 306 indicates that the distance to the line segments 308 and 310 that are orthogonal to the shafts 62 and 64 and pass through the centers of the bearings 68 and 72 (line segments that divide the bearings 68 and 72 into two in the radial direction) 308 and 310 gradually increases as the distance from the shafts 62 and 64 increases. It is supposed to be an inclined surface that becomes larger. In other words, the retainer contact surfaces 304 and 306 of the bearing outer rings 272 and 284 are inclined toward the inner diameter side toward the balls 300 and 302.

  The retainers 280 and 288 are members for preventing the axial displacement of the shafts 62 and 64 and suppressing the misalignment of the belt 94 (see FIG. 1). The retainers main bodies 312 and 314, the retainer main bodies 312, Retainer main body 312 is formed on the lower surface of 314 so as to constitute bolt fastening portions 320 and 322 to which bolts 276A and 276B are fastened, and convex portions projecting toward retainer contact surfaces 304 and 306 of bearing outer rings 272 and 284. , 314, bearing outer ring pressing portions 324 and 326 bent in an L shape from the tip end portion. These retainers 280 and 288 are provided on the bearing outer rings 272 and 284 in which the corners of the L-shaped bearing outer ring pressing parts 324 and 326 are the inclined surfaces in a state where the bolts 276A and 276B are fastened to the bolt fastening parts 320 and 322, respectively. The bearings 68 and 72 are installed obliquely so as to contact the retainer contact surfaces 304 and 306.

  As described above, in the belt-type continuously variable transmission 24 according to the present embodiment, the retainer contact surfaces 304 and 306 of the bearing outer rings 272 and 284 are orthogonal to the shafts 62 and 64 as the distance from the shafts 62 and 64 increases. The inclined surfaces are gradually increased in distance to the line segments 308 and 310 passing through the centers of the bearings 68 and 72, and the bearing outer ring pressing portions 324 and 326 of the retainers 280 and 288 are used as the retainer contact surfaces 304 of the bearing outer rings 272 and 284, respectively. The retainers 280 and 288 have a stepped shape that is bent in an L shape from the distal end portions of the retainer main bodies 312 and 314 so as to form convex portions that project toward 306, so that the retainers 280 and 288 have bolts 276 A and bolts 276 A, In the state where 276B is fastened, the corners of the L-shaped bearing outer ring pressing portions 324 and 326 are inclined surfaces. Will contact the retainer contact surface 304, 306 of the bearing outer ring 272,284 which are. Therefore, as indicated by arrows in FIG. 3, the load direction of the retainers 280 and 288 to the bearing outer rings 272 and 284 is an oblique direction on the outer diameter side. As a result, the deterioration of the roundness of the raceway surfaces of the bearing outer rings 272 and 284 can be suppressed.

  The present invention is not limited to the above embodiment.

  In the above embodiment, the retainers 280 and 288 are bearings in which the corners of the L-shaped bearing outer ring pressing portions 324 and 326 are inclined surfaces in a state where the bolts 276A and 276B are fastened to the bolt fastening portions 320 and 322. The example in which the bearings 68 and 72 are installed obliquely so as to contact the retainer contact surfaces 304 and 306 of the outer rings 272 and 284 has been described. However, the present invention is not limited to such a configuration. As shown in FIG. 4, the retainers 280 and 288 are bearings in which corners of L-shaped bearing outer ring pressing portions 324 and 326 are inclined surfaces in a state where the bolts 276 </ b> A and 276 </ b> B are fastened to the bolt fastening portions 320 and 322. Even if it is installed horizontally with respect to the bearings 68 and 72 so as to be in contact with the retainer contact surfaces 304 and 306 of the outer rings 272 and 284, the same operations and effects are obtained.

  Further, in the above embodiment, the retainer main body 312 is configured so that the bearing outer ring pressing portions 324 and 326 of the retainers 280 and 288 form convex portions protruding toward the retainer contact surfaces 304 and 306 of the bearing outer rings 272 and 284. , 314 was described as an example of a stepped shape bent from an end portion into an L shape. However, the present invention is not limited to such a configuration. As shown in FIG. 5, the bearing outer ring pressing portions 324 and 326 of the retainers 280 and 288 bulge in an arc shape so as to form convex portions protruding toward the retainer contact surfaces 304 and 306 of the bearing outer rings 272 and 284. The outer ring bearings 280 and 288 are formed into inclined surfaces at the tops of the bulging portions of the bearing outer ring pressing portions 324 and 326 when the bolts 276A and 276B are fastened to the bolt fastening portions 320 and 322. Even if it is installed horizontally with respect to the bearings 68 and 72 so as to be in contact with the retainer contact surfaces 304 and 306 of 272 and 284, the same operation and effect can be obtained. Of course, in this modified example, the retainers 280 and 288 are bearings in which the tops of the bulging portions of the bearing outer ring pressing portions 324 and 326 are inclined surfaces in a state where the bolts 276A and 276B are fastened to the bolt fastening portions 320 and 322. You may make it install with an inclination with respect to the bearings 68 and 72 so that the retainer contact surfaces 304 and 306 of the outer ring | wheels 272 and 284 may be contacted.

  It goes without saying that various design changes and modifications can be made within the scope of the claims attached to this specification.

24 belt type continuously variable transmission 62 primary shaft (pulley shaft)
64 Secondary shaft (pulley shaft)
68, 72 Bearing 272, 274 Outer ring 274, 286 Recessed part 280, 288 Retainer 304, 306 Retainer contact surface 308, 310 Line segment 312, 314 Retainer main body 320, 322 Bolt fastening part 324, 326 Bearing outer ring pressing part

Claims (1)

A belt type continuously variable transmission in which a bearing outer ring for a pulley shaft is housed in a recess formed in the case, and the bearing outer ring is pressed from the outside of the recess by using a retainer fixed to the case to be positioned and fixed in the axial direction. There,
The retainer contact surface of the bearing outer ring is an inclined surface in which the distance to a line segment perpendicular to the pulley shaft and passing through the bearing center gradually increases as the distance from the pulley shaft increases.
The belt-type continuously variable transmission, wherein the bearing outer ring pressing portion of the retainer has a convex portion protruding toward a retainer contact surface of the bearing outer ring.

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