JP2018155386A - Lubrication structure of power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To appropriately supply lubrication oil supplied to a space part of a bottomed hole from the oil passage of a rotational axis to the outside of the rotational axis regardless of existence of an oil draining passage for making hardening oil flow out.SOLUTION: An opening part to an axis center hole 90 of an oil draining passage 92 is made open to a side inner than an oil hole 88 in a radius direction having a rotational axis core S as a center, and thereby risk that lubrication oil supplied to a space part 82 via the oil hole 88 from an oil passage 84 of an input axis (rotational axis) 22 is flown to the outer peripheral side as it is via centrifugal force and is supplied to the outside of the input axis 22 is increased, and an amount of the lubricant oil flown outside of a fixed sheave 60a through an oil draining passage 92 open to a side inner than the oil hole 88. The hardening oil when subjecting the fixed sheave 60a to hardening treatment in a perpendicular posture is flown out to the outside through the oil draining passage 92 by mounting the oil draining passage 92 so as to open to the inner peripheral surface of the axis core hole 90, so that operation for removing the hardening oil becomes unnecessary or simple.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a lubricating structure for a power transmission device in which a variable pulley and a rotating shaft are arranged on the same rotating shaft.

  (a) The same rotation as the stationary sheave with a space remaining between the variable pulley having a bottomed hole concentric with the rotational axis at one end of the stationary sheave and the bottom of the bottomed hole An oil passage provided on the shaft center and having an oil passage provided in the axial direction communicates with the space portion, and (b) lubricating oil supplied from the oil passage to the space portion is provided. A power transmission device that is supplied to the outside of the rotary shaft by centrifugal force and used for lubrication is known. The apparatus described in Patent Document 1 is an example, and the fixed sheave (52) of the primary pulley (50) and the input shaft (3a) are disposed on the same rotational axis so as to be relatively rotatable, and the input shaft The lubricating oil supplied from the oil passage (3b) provided in the oil passage (52c) provided in the fixed sheave to the outside of the input shaft is further supplied from the gap (GP2) ( (See FIG. 2). In this case, the oil passage (52c) corresponds to a bottomed hole, and the input shaft (3a) corresponds to a rotating shaft.

JP 2001-12570 A

  By the way, although not yet known, in order to prevent the quenching oil when quenching the fixed sheave from remaining in the bottomed hole, an oil drain passage communicating with the outside of the fixed sheave may be provided at the bottom of the bottomed hole. Conceivable. For example, when a shaft center hole (center hole) is provided at the bottom of the bottomed hole for centering such as cutting, an oil drain passage is provided so as to open on the inner peripheral surface of the shaft center hole. However, since this oil drain passage communicates with the space portion, part of the lubricating oil supplied to the space portion from the oil passage of the rotary shaft also flows out of the fixed sheave from the oil drain passage. There is a risk that the amount of lubricating oil supplied to the lubrication site such as the external bearing of the engine will be insufficient.

  The present invention has been made against the background of the above circumstances, and the object of the present invention is to provide a space portion of the bottomed hole from the oil passage of the rotating shaft regardless of the presence of an oil drain passage for allowing quenching oil to flow out. The lubricating oil supplied to is to be appropriately supplied to the outside of the rotating shaft.

  In order to achieve this object, the present invention provides: (a) a space portion between a variable pulley in which a bottomed hole is provided concentrically with a rotation axis at one end of a fixed sheave, and a bottom of the bottomed hole. And a rotating shaft that is disposed on the same rotational axis as the fixed sheave with the oil passage provided in the axial direction in communication with the space portion, and (b) the oil In the lubricating structure of the power transmission device in which the lubricating oil supplied from the road to the space portion is supplied to the outside of the rotating shaft by centrifugal force and used for lubrication, (c) the oil path extends from the rotating shaft center. While being communicated with the space through an oil hole provided at an eccentric position, (d) the bottom of the bottomed hole is provided with an axial hole concentric with the rotational axis. In addition, an oil drainage passage is provided so as to penetrate from the inner peripheral surface of the axial hole to the outside of the fixed sheave. (E) An opening portion of the oil drainage passage with respect to the axial hole is opened inward of the oil hole in a radial direction centering on the rotation axis.

  In such a lubrication structure of the power transmission device, the opening portion with respect to the shaft center hole of the oil drain passage is opened radially inward from the oil hole, so that the oil passage from the rotation shaft passes through the oil hole. Lubricating oil supplied to the space is more likely to flow to the outer peripheral side as it is due to centrifugal force and to be supplied to the outside of the rotating shaft, and from the oil drainage path that opens inside the oil hole, The amount of lubricating oil flowing out is reduced. In addition, the oil drainage path is provided in the shaft hole provided at the bottom of the bottomed hole, so that the quenching oil when quenching the fixed sheave can flow out from the oil drainage path to the outside. The work for removing is unnecessary or simple. That is, the hardened oil in the bottomed hole and the shaft hole of the fixed sheave to be hardened is appropriately discharged to the outside from the oil drainage passage and removed without impairing the supply of lubricating oil from the space to the outside of the rotating shaft. be able to.

1 is a skeleton diagram illustrating an example of a vehicle power transmission device having a lubrication structure to which the present invention is applied. FIG. 2 is a cross-sectional view specifically showing a connecting portion between a fixed sheave of a primary pulley and an input shaft of the belt type continuously variable transmission of FIG. 1. It is sectional drawing which showed the fixed sheave independently, and is the figure which showed the state hold | maintained at the vertical attitude | position when hardening processing is performed. It is a figure explaining the other Example of this invention, and is sectional drawing corresponding to FIG.

  The present invention is preferably applied to a lubricating structure for a power transmission device for a vehicle having a belt-type continuously variable transmission, but can also be applied to a lubricating structure for a power transmission device other than for a vehicle. The variable pulley may be a primary pulley or a secondary pulley, and an input shaft and an output shaft are connected to a bottomed hole provided at one end portion of the fixed sheave through a spline fitting or the like so as not to be relatively rotatable. The rotary shaft provided with an oil passage in the axial direction may be an input shaft or an output shaft.For example, the input shaft is inserted into the bottomed hole of the fixed sheave via a planetary gear type forward / reverse switching device or a transmission. In addition to the input shaft, the rotary shaft having an axial oil passage may be provided so as to pass through the input shaft and be arranged to be rotatable relative to the fixed sheave. Is possible. The oil path of the rotating shaft is provided on the axis of the rotating shaft, for example, but may be provided at a position eccentric from the axis. Further, the lubricating oil is directly supplied to the oil passage from, for example, an oil pump disposed concentrically with the rotating shaft, but the lubricating oil may be supplied from a valve body having a hydraulic control valve or the like.

  The oil hole that connects the oil passage of the rotating shaft and the space portion is provided, for example, in a cap attached to the opening of the oil passage, but it is also possible to directly provide an oil hole having a smaller diameter than the oil passage in the rotating shaft. . The positional relationship between the oil hole and the opening of the oil drain passage is such that the radial dimension up to the maximum diameter portion of the opening of the oil drain passage is, for example, the minimum diameter of the oil hole in the radial direction around the rotation axis. Although it is smaller than the radial dimension to the portion, at least the radial dimension to the center position of the opening of the oil drainage path may be smaller than the radial dimension to the center position of the oil hole. Lubricating oil supplied to the space is, for example, a gap between the bottomed hole and the rotating shaft, such as a backlash for spline fitting, an axial direction provided on the inner peripheral surface of the bottomed hole or the outer peripheral surface of the rotating shaft. Although it is supplied to the outside of the rotating shaft from a groove or the like, it may be supplied to the outside of the rotating shaft from a communication oil passage provided in the fixed sheave.

  In the bottom portion of the bottomed hole, the oil rebound that rebounds the lubricating oil to the axial linear position of the oil hole so that the lubricant discharged from the oil hole is prevented from entering the oil drain passage. It is desirable to provide a wall. For example, in the case where an axial center hole having a radius smaller than the radial dimension from the rotational axis to the oil hole is provided, the oil rebound wall has a rotational axis on the outer peripheral portion of the bottomed hole than the axial center hole. It may be just a flat surface perpendicular to the heart. Further, when the axial hole including the position on the straight line in the axial direction of the oil hole is provided, the axial hole may be a tapered hole having a smaller diameter on the tip side (bottom side). That is, the lubricating oil adhering to the inner peripheral surface (inclined surface) of the tapered hole is caused to flow so as to be rebounded to the large-diameter side, that is, the bottomed hole side by centrifugal force, and the inflow to the oil drain passage is suppressed. The inner peripheral surface of the tapered hole functions as an oil splash wall. The axial hole is not limited to a tapered hole but may be a cylindrical hole having a constant diameter.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following embodiments, the drawings are appropriately simplified or modified for explanation, and the dimensional ratios, shapes, and the like of the respective parts are not necessarily drawn accurately.

  FIG. 1 is a skeleton diagram illustrating the configuration of a vehicular power transmission device 10 having a lubricating structure to which the present invention is applied. FIG. 1 is an exploded view showing a plurality of parallel axes located in one plane. It is. This vehicle power transmission device 10 is a transaxle that is preferably employed in an FF (front engine / front drive) type vehicle, and the output of an engine 12 such as an internal combustion engine that is a power source for traveling is a fluid transmission. The torque is transmitted from the torque converter 14 serving as a device to the differential gear device 18 via the automatic transmission 16, and is distributed to the left and right drive wheels 20L and 20R. The torque converter 14 includes a pump impeller 14p connected to the crankshaft of the engine 12 and a turbine impeller 14t connected to the input shaft 22 of the automatic transmission 16, and transmits power through a fluid. Further, it is directly connected via a lock-up clutch 15. The pump impeller 14p is provided with a mechanical oil pump 17, and is used as a hydraulic pressure source by being driven to rotate by the engine 12 and outputting hydraulic pressure.

  The automatic transmission 16 is connected to an input shaft 22 provided integrally with a turbine shaft that is an output rotating member of the torque converter 14, a belt-type continuously variable transmission 24 connected to the input shaft 22, and also connected to the input shaft 22. A forward / reverse switching device 26 and a gear transmission mechanism 28 provided in parallel with the belt-type continuously variable transmission 24, an output shaft 30 that is a common output rotating member of the belt-type continuously variable transmission 24 and the gear transmission mechanism 28, a deceleration A gear device 32 is provided, and a small-diameter gear 34 of the reduction gear device 32 is meshed with a ring gear 36 of the differential gear device 18. The gear transmission mechanism 28 corresponds to a gear transmission mechanism. In the automatic transmission 16 configured as described above, the output of the engine 12 is transmitted from the torque converter 14 to the output shaft 30 via the belt type continuously variable transmission 24 or via the belt type continuously variable transmission 24. Without being transmitted to the output shaft 30 via the forward / reverse switching device 26 and the gear speed change mechanism 28, it is further transmitted to the left and right drive wheels 20L, 20R via the reduction gear device 32 and the differential gear device 18.

  That is, the automatic transmission 16 of the present embodiment includes a first power transmission path TP1 that transmits the output of the engine 12 from the input shaft 22 to the output shaft 30 via the forward / reverse switching device 26 and the gear transmission mechanism 28, and the engine 12. , And a second power transmission path TP2 for transmitting the output from the input shaft 22 to the output shaft 30 via the belt-type continuously variable transmission 24, and the transmission of such power according to the traveling state of the vehicle. The routes TP1 and TP2 are switched. Therefore, the automatic transmission 16 includes a forward clutch C1 and a reverse brake B1 as a first connecting / disconnecting device for connecting / disconnecting (connecting / disconnecting) the power transmission in the first power transmission path TP1, and a second power transmission. And a CVT travel clutch C2 as a second connecting / disconnecting device for connecting / disconnecting power transmission in the route TP2. The first power transmission path TP1 further includes a meshing clutch Cd as a meshing type connecting / disconnecting device in series with the forward clutch C1 and the gear transmission mechanism 28, specifically, on the downstream side thereof. Is provided.

  The forward / reverse switching device 26 is mainly composed of a double pinion type planetary gear device, and the carrier 26c is integrally connected to the input shaft 22 so that the sun gear 26s can rotate relative to the input shaft 22 coaxially. While the ring gear 26r is selectively stopped via the reverse brake B1, the carrier 26c and the sun gear 26s are selectively connected via the forward clutch C1. It has come to be. When the forward clutch C1 is engaged and the reverse brake B1 is released, the input shaft 22 is directly connected to the small diameter gear 42 to establish the forward power transmission state, and the reverse brake B1 is engaged. When the forward clutch C1 is released and the small-diameter gear 42 is released, the small-diameter gear 42 is rotated in the reverse direction with respect to the input shaft 22, and the reverse power transmission state is established. Further, when both the forward clutch C1 and the reverse brake B1 are released, a neutral state is established in which power transmission is interrupted. Each of the forward clutch C1 and the reverse brake B1 is a multi-plate friction engagement device in which a plurality of friction materials are frictionally engaged by a hydraulic cylinder.

  The gear transmission mechanism 28 is provided with a small-diameter gear 42, a large-diameter gear 46 that is provided so as not to rotate relative to the counter shaft 44 and meshed with the small-diameter gear 42, and a coaxial shaft relative to the counter shaft 44. A small-diameter idler gear 48 is provided. A meshing clutch Cd is provided between the counter shaft 44 and the idler gear 48, and power transmission therebetween is connected and disconnected. The meshing clutch Cd is provided with a synchromesh mechanism (synchronizing mechanism) such as a synchronizer ring, and the clutch hub sleeve 50 is moved in the connecting direction which is the left direction in FIG. 1 by a clutch switching device such as a hydraulic cylinder. When the idler gear 48 is rotated synchronously with the counter shaft 44 via the synchronizer ring and the clutch hub sleeve 50 is further moved, the idler gear 48 is connected via spline teeth provided on the inner peripheral surface of the clutch hub sleeve 50. The idler gear 48 is connected to the counter shaft 44.

  The idler gear 48 is meshed with a large-diameter gear 58 provided on the output shaft 30, and either the forward clutch C1 or the reverse brake B1 is engaged, and the meshing clutch Cd is connected. As a result, the output of the engine 12 is transmitted from the input shaft 22 to the output shaft 30 via the forward / reverse switching device 26, the gear transmission mechanism 28, the idler gear 48, and the large-diameter gear 58 in this order. The transmission path TP1 is established. Note that it is possible to assume that a gear shift (deceleration) is also performed between the small-diameter idler gear 48 and the large-diameter gear 58, and that the gear transmission mechanism 28 is configured.

  The belt type continuously variable transmission 24 includes a primary pulley 60 having a variable effective diameter connected to the input shaft 22, a secondary pulley 64 having a variable effective diameter connected to a pulley rotation shaft 62 coaxial with the output shaft 30, and A transmission belt 66 wound between the pair of pulleys 60 and 64 is provided, and power is transmitted through friction between the pair of pulleys 60 and 64 and the transmission belt 66. The pair of pulleys 60 and 64 are fixed sheaves 60a and 64a connected to the input shaft 22 and the pulley rotation shaft 62 so as to be able to transmit power, respectively, and the input shaft 22 and the pulley rotation shaft 62 cannot rotate relative to each other. The movable sheaves 60b and 64b are provided so as to be movable in the axial direction, and hydraulic cylinders 60c and 64c are provided as hydraulic actuators that apply thrust to change the V groove width therebetween. Then, for example, by controlling the primary hydraulic pressure supplied to the hydraulic cylinder 60c, the width of the V-grooves of the pulleys 60 and 64 is changed, the engagement diameter (effective diameter) of the transmission belt 66 is changed, and the gear ratio is continuously increased. Can be changed. Further, by controlling the secondary hydraulic pressure supplied to the hydraulic cylinder 64c, the belt clamping pressure is adjusted so that the transmission belt 66 does not slip.

  The output shaft 30 is disposed so as to be coaxially rotatable with respect to the pulley rotation shaft 62, and the CVT traveling clutch C2 provided between the output shaft 30 and the secondary pulley 64 is used to The power transmission between the output shaft 30 and the secondary pulley 64 is connected / disconnected. When the CVT travel clutch C2 is engaged, the output of the engine 12 is transmitted from the input shaft 22 to the output shaft 30 via the belt-type continuously variable transmission 24, and the second power transmission path TP2 Is established. The CVT travel clutch C2 is a multi-plate friction engagement device in which a plurality of friction materials are frictionally engaged by a hydraulic cylinder.

  FIG. 2 is a cross-sectional view specifically showing a connecting portion between the fixed sheave 60 a of the primary pulley 60 and the input shaft 22 of the belt-type continuously variable transmission 24. In FIG. 2, the fixed sheave 60 a and the input shaft 22 are disposed concentrically with the common rotation axis S, and are relatively movable in the axial direction via the spline fitting portion 70 and around the rotation axis S. They are connected so that they cannot rotate relative to each other. The axis of the input shaft 22 and the axis of the fixed sheave 60a basically coincide with the rotation axis S. The fixed sheave 60a is integrally provided with a shaft portion 72 and a flange portion 74, and the movable sheave 60b is spline-fitted on the outer peripheral side of the shaft portion 72 so as to be relatively movable in the axial direction and not to be rotatable around the rotation axis S. Are combined. One end portion of the shaft portion 72, that is, the end portion connected to the input shaft 22, is supported by the case 78 so as to be rotatable around the rotation axis S via the bearing 76, and is rotated at one end portion thereof. A bottomed connecting hole 80 is provided concentrically with the shaft center S, and inner spline teeth of the spline fitting portion 70 are provided on the inner peripheral surface of the connecting hole 80. The connecting hole 80 corresponds to a bottomed hole.

  One end of the input shaft 22, that is, the end connected to the fixed sheave 60 a has a cylindrical shape with an outer diameter slightly smaller than that of the connection hole 80, and the spline fitting is performed on the outer peripheral surface. Outer spline teeth of the portion 70 are provided, and are spline-fitted so as to be relatively movable in the axial direction with respect to the connecting hole 80 and not to be rotatable around the rotation axis S. The input shaft 22 is also supported rotatably around the rotation axis S through a bearing (not shown). The input shaft 22 is spline-fitted with a predetermined space 82 left between the bottom of the connection hole 80 and is provided in the axial direction on the input shaft 22 on the axis concentric with the rotation axis S. The oil passage 84 thus communicated with the space portion 82. Lubricating oil is directly supplied to the oil passage 84 from the oil pump 17 that is driven to rotate about the rotation axis S, and the oil passage 84 opens at one end of the input shaft 22. A cap 86 is fixed by press-fitting or the like, and is communicated with the space portion 82 through an oil hole 88 provided in the cap 86. Accordingly, the lubricating oil in the oil passage 84 is supplied to the space portion 82 at a predetermined flow rate through the oil hole 88, and further flows out of the input shaft 22 from a gap such as a backlash of the spline fitting portion 70 by centrifugal force. As a result, the spline fitting portion 70, the bearing 76, and the friction material of the reverse brake B1 are used for lubrication. A plurality of oil holes 88 are provided at equiangular intervals so that the positions of the oil holes 88 are eccentric from the rotation axis S, that is, the radial dimension (radius) from the rotation axis S is located on the circumference of a. ing. In the present embodiment, the primary pulley 60 corresponds to a variable pulley, and the input shaft 22 corresponds to a rotating shaft.

  The connecting hole 80 of the fixed sheave 60a is provided with an axial hole 90 on the rotational axis S at the bottom. The shaft hole 90 can be used as a center hole for centering when performing cutting or the like on the fixed sheave 60a, for example. For example, as shown in FIG. 3, the fixed sheave 60a is subjected to quenching treatment with quenching oil in a vertical posture in which the collar portion 74 is positioned upward. Quenching oil remains in the hole 80 and the axial hole 90. For this reason, in this embodiment, the oil draining path 92 is provided in a direction perpendicular to the rotation axis S (radial direction) so as to penetrate from the inner peripheral surface on the bottom side of the shaft hole 90 to the outside of the shaft portion 72. The quenching oil in the connecting hole 80 and the shaft hole 90 is discharged from the oil draining path 92 to the outside. The oil draining path 92 may be one, but a plurality of oil draining paths 92 may be provided around the rotation axis S. The oil draining path 92 is inclined from the direction perpendicular to the rotational axis S to the opposite side to the flange 74 (that is, the lower side in FIG. 3) as it goes from the axial hole 90 to the outside of the shaft part 72. It can also be provided.

  On the other hand, when the belt-type continuously variable transmission 24 having the fixed sheave 60 a provided with the oil draining path 92 is used in the vehicle power transmission device 10, the oil draining path 92 is formed in the space portion 82 through the shaft hole 90. Therefore, the lubricating oil supplied from the oil passage 84 of the input shaft 22 to the space 82 may also enter the shaft hole 90 and flow out of the fixed sheave 60a from the oil drain passage 92. There is. On the other hand, in this embodiment, the radial dimension b to the center position of the opening where the oil drain passage 92 opens in the inner peripheral surface of the axial hole 90 in the radial direction centered on the rotational axis S is: It is smaller than the radial dimension a up to the center position of the oil hole 88. Since the axial hole 90 is a cylindrical hole having a constant diameter, and the oil drain passage 92 is opened on the inner peripheral surface of the axial hole 90, the radial dimension b of the opening is the radius of the axial hole 90. And the radius of the axial hole 90 is made smaller than the radial dimension a. In this embodiment, the radial dimension b is determined to be smaller than the radial dimension up to the minimum diameter portion of the oil hole 88 by the difference dimension d. Since the lubricating oil supplied from the oil hole 88 into the space portion 82 is caused to flow to the outer peripheral side by centrifugal force, the axial hole provided on the inner side of the oil hole 88 in the radial direction around the rotational axis S. It is possible to prevent the oil from entering the inside 90 and flowing out from the oil drainage path 92 to the outside of the fixed sheave 60a.

  Further, when the radial dimension b, that is, the radius of the axial hole 90 is determined to be smaller than the radial dimension up to the minimum diameter portion of the oil hole 88 by a difference dimension d, the axial position of the oil hole 88 on the straight line Has a bottom surface 94 of the connecting hole 80, and even when the lubricating oil is discharged linearly in the axial direction from the oil hole 88, it bounces back against the bottom surface 94 and enters the shaft hole 90. Is suppressed. The bottom surface 94 is a flat surface perpendicular to the rotation axis S, and the lubricating oil is allowed to flow along the bottom surface 94 to the outer peripheral side according to the centrifugal force. The bottom surface 94 functions as an oil splash wall.

  The two-dot chain line in FIG. 2 is a cross-sectional shape of a conventional shaft center hole, and is provided with a relatively large diameter shaft center hole for the purpose of weight reduction and the like. Bigger than. For this reason, when the oil drain passage 92 is provided so as to communicate with the outside through the shaft hole, a part of the lubricating oil supplied from the oil passage 84 of the input shaft 22 to the space portion 82 is fixed from the oil drain passage 92 to the fixed sheave. There is a risk that the amount of lubricating oil that flows out of 60a and is supplied to the spline fitting portion 70, the bearing 76, and the like outside the input shaft 22 will be insufficient.

  Thus, in the vehicle power transmission device 10 of the present embodiment, the opening portion of the oil drain passage 92 with respect to the axial hole 90 opens inward of the oil hole 88 in the radial direction centering on the rotation axis S. Therefore, the lubricating oil supplied from the oil passage 84 of the input shaft 22 to the space 82 via the oil hole 88 is directly flowed to the outer peripheral side by centrifugal force and supplied to the outside of the input shaft 22. The amount of lubricating oil that flows out of the fixed sheave 60a from the oil drain passage 92 that opens to the inside of the oil hole 88 is reduced. Further, the oil drainage passage 92 is provided so as to open to the inner peripheral surface of the shaft center hole 90 provided at the bottom of the connection hole 80, so that when the fixed sheave 60a is quenched in the vertical posture shown in FIG. The quenching oil is allowed to flow out from the oil drain passage 92, and the work for removing the quenching oil becomes unnecessary or simple. That is, the hardened oil in the coupling hole 80 and the shaft center hole 90 of the fixed sheave 60a to be hardened is appropriately removed from the oil draining path 92 to the outside without impairing the supply of the lubricating oil from the space 82 to the outside of the input shaft 22. Can be drained and removed.

  Next, another embodiment of the present invention will be described. In the following embodiments, parts that are substantially the same as those in the above embodiments are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the above embodiment, the cylindrical shaft center hole 90 having a constant diameter is provided. However, as shown in FIG. 4, the tapered shaft center hole 100 having a smaller diameter on the tip side (bottom side) is provided as the rotation center. It can also be provided on an axis concentric with S. Also in this case, the oil draining path 92 is provided so as to open to the inner peripheral surface of the shaft center hole 100, but in the radial direction centering on the rotation axis S, the oil draining path 92 is located inside the shaft center hole 100. The opening position of the oil draining path 92 is determined so that the radial dimension b to the center position of the opening opening on the peripheral surface is smaller than the radial dimension a to the center position of the oil hole 88. In particular, the opening position of the oil drain passage 92 is determined such that the radial dimension to the maximum diameter portion of the opening of the oil drain passage 92 is smaller than the radial dimension to the minimum diameter portion of the oil hole 88. Is desirable. The shaft hole 100 can be used as a center hole for centering when performing cutting or the like on the fixed sheave 60a, for example.

  Also in this embodiment, the lubricating oil supplied from the oil passage 84 of the input shaft 22 through the oil hole 88 into the space 82 is directly flowed to the outer peripheral side by centrifugal force and supplied to the outside of the input shaft 22. The amount of lubricating oil flowing out of the fixed sheave 60a from the oil drain passage 92 that opens to the inside of the oil hole 88 is reduced.

  On the other hand, the radial dimension of the opening of the taper-shaped axial hole 100 is larger than the radial dimension a of the oil hole 88, and the inner peripheral surface (tapered) of the axial hole 100 is on the straight line in the axial direction of the oil hole 88. The lubricating oil discharged linearly in the axial direction from the oil hole 88 adheres to the inner peripheral surface of the shaft center hole 100. This lubricating oil may flow directly to the bottom side of the shaft hole 100 and enter the oil draining path 92. However, the lubricating oil has a large diameter along the inner peripheral surface of the shaft hole 100 due to centrifugal force. It is made to flow so that it bounces back to the hole 80 side, and it is suppressed that it flows out from the oil draining path 92 outside. That is, in the case of the conventional shaft center hole indicated by the two-dot chain line, the inner peripheral surface is a cylindrical surface parallel to the rotation axis S, so that the action of rebounding to the connecting hole 80 side cannot be obtained. The amount of lubricating oil that flows out to the outside increases. The inner peripheral surface of the axial hole 100 functions as an oil splash wall.

  As mentioned above, although the Example of this invention was described in detail based on drawing, these are one Embodiment to the last, This invention is implemented in the aspect which added the various change and improvement based on the knowledge of those skilled in the art. be able to.

  10: Vehicle power transmission device (power transmission device) 22: Input shaft (rotary shaft) 60: Primary pulley (variable pulley) 60a: Fixed sheave 80: Connection hole (bottomed hole) 82: Space portion 84: Oil passage 88 : Oil hole 90, 100: Center hole 92: Oil drainage path S: Center of rotation

Claims (1)

On the same rotational axis as the fixed sheave with a space between the variable pulley having a bottomed hole concentric with the rotational axis at one end of the fixed sheave and the bottom of the bottomed hole And an oil passage provided in an axial direction has a rotating shaft communicated with the space portion,
In the lubricating structure of the power transmission device, the lubricating oil supplied from the oil passage to the space is supplied to the outside of the rotating shaft by centrifugal force and used for lubrication.
While the oil passage is communicated with the space through an oil hole provided at a position eccentric from the rotational axis,
A shaft center hole is provided concentrically with the rotational axis at the bottom of the bottomed hole, and an oil drain passage is provided so as to penetrate from the inner peripheral surface of the shaft hole to the outside of the fixed sheave. And
The lubrication structure for a power transmission device, wherein an opening portion of the oil drainage passage with respect to the axial hole is opened inward of the oil hole in a radial direction centering on the rotation axis.

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