JP5817416B2 - Bearing lubricator - Google Patents

Description

  The present invention relates to a bearing lubrication device.

  Conventionally, a configuration has been disclosed in which oil is supplied into a shaft, the oil is deflected by a spacer, and the oil is supplied to a rolling element of a rolling bearing (for example, Patent Document 1).

  On the other hand, a configuration has been disclosed in which an oil guide path is provided between an inner race (inner ring) of a bearing and a shaft to supply oil (for example, Patent Document 2).

JP 2003-294044 A JP 2000-283272 A

  In order to suitably suppress the wear of the bearing, it is desirable that oil can be supplied to the rolling elements of the bearing as described in Patent Document 1, and further, oil can be supplied between the inner ring of the bearing and the shaft.

  Here, considering the case where the configuration for supplying oil between the inner ring of the bearing and the shaft described in Patent Document 2 is applied to Patent Document 1, oil is supplied between the shaft and the inner ring of the bearing. In addition, since it is necessary to form a guide path in the shaft, the strength of the shaft may not be ensured.

  The present invention has been made in view of the above circumstances, and provides a bearing lubrication device capable of suppressing the wear of the bearing and ensuring the strength of the shaft supported by the bearing. With the goal.

  In order to solve the above problems, a bearing lubrication apparatus according to the present invention is a bearing lubrication apparatus for lubricating a bearing that supports a shaft, and is capable of discharging oil radially outward from the inside of the shaft. The formed oil passage and the oil discharged from the oil passage toward the outer side in the radial direction of the shaft are bounced back and scattered toward the contact portion between the inner ring of the bearing and the shaft, and the contact portion A first guide for supplying the oil to the shaft, and the oil discharged from the oil passage toward the radially outer side of the shaft bounces back toward the rolling element of the bearing and scatters the oil to the rolling element. A second guide to be supplied, wherein the first guide and the second guide are arranged along a circumferential direction around an axis of the shaft.

  In the bearing lubrication apparatus, it is preferable that the first guide and the second guide have different radial positions from the shaft center of the shaft.

  In the bearing lubrication apparatus described above, it is preferable that the first guide and the second guide have different reflection surface inclination angles that repel oil discharged from the oil passage.

  According to the bearing lubrication device of the present invention, the first guide focuses oil on the contact portion between the inner ring and the shaft of the bearing, and the second guide focuses oil on the rolling elements of the bearing. Since it supplies, abrasion of a 1st bearing can be suppressed suitably. In addition, since it is not necessary to form a guide path on the shaft in order to supply oil to the gap between the bearing and the shaft as in the prior art, the strength of the shaft can be ensured. As a result, there is an effect that the strength of the shaft can be secured while suppressing wear of the bearing.

FIG. 1 is a diagram showing a configuration of a trans-vehicle for a hybrid vehicle to which a bearing lubrication device according to a first embodiment of the present invention is applied. FIG. 2 is an enlarged view of a portion related to the bearing lubrication device according to the first embodiment of the present invention in the transaxle shown in FIG. FIG. 3 is a schematic view showing the shape of the guide member in FIG. 2 as viewed in the axial direction. FIG. 4 is a schematic view showing the shape of the guide member in the first modification of the first embodiment. FIG. 5 is a schematic view showing the shape of the guide member in the second modification of the first embodiment. FIG. 6 is a schematic view showing the shape of the guide member in the third modification of the first embodiment. FIG. 7 is a schematic view showing the shape of the guide member in the fourth modification of the first embodiment. FIG. 8 is a diagram showing a configuration of a bearing lubricating device according to the second embodiment of the present invention. FIG. 9 is a diagram illustrating an example of a configuration in the case where the present invention is applied to lubrication of a bearing that is supported by an intermediate shaft portion.

  Embodiments of a bearing lubrication device according to the present invention will be described below with reference to the drawings. In the following drawings, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will not be repeated.

(First embodiment)
First, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a diagram showing a configuration of a trans-vehicle 100 for a hybrid vehicle to which a bearing lubrication device 5 according to the present embodiment is applied, and FIG. 2 is an embodiment of the trans-vehicle 100 shown in FIG. FIG. 3 is an enlarged view of a portion related to the lubricating device 5 of the bearing according to FIG. 3, and FIG. 3 is a schematic view showing the shape of the guide member in FIG.

  As shown in FIG. 1, a bearing lubrication device 5 according to this embodiment is mounted on a hybrid vehicle that travels using a motor 2 and an engine (disposed on the right side of FIG. 1 and not shown) as a power source. It is applied in the transaxle 100.

  The transaxle 100 includes a motor 2, an MG shaft 20, a counter shaft 6 and elements such as an input shaft, a generator, a differential mechanism, and an output shaft (not shown in FIG. 1) in a case 1 that is an outer shell member. Transaxle 100 connects the engine and driving wheels via a plurality of shafts including an input shaft, MG shaft 20, counter shaft 6, and output shaft that are arranged in parallel in case 1 and connected to each other. It has a configuration.

  The input shaft is an input shaft to which engine power is input. The differential mechanism decelerates the power of the engine and the motor 2 and transmits it to the left and right drive wheels via the output shaft.

  The counter shaft 6 is rotatably supported by the case 1 via a bearing. The counter shaft 6 includes a counter driven gear 7 and a final drive gear 8. The counter driven gear 7 meshes with the counter drive gear of the input shaft.

  The MG shaft 20 is a rotating shaft of the motor 2. The motor 2 has both a function (power running function) as an electric motor driven by the supply of electric power and a function (regeneration function) as a generator that converts mechanical energy into electric energy. As the motor 2, for example, an AC synchronous motor generator can be used. The motor 2 has a stator 2A as a stator fixed to the case 1, and a rotor 2B as a rotor disposed inside the stator 2A.

  The MG shaft 20 has a first shaft portion 21 and a second shaft portion 22. The second shaft portion 22 is disposed closer to the engine side in the axial direction than the first shaft portion 21. The first shaft portion 21 is connected to the rotor 2B. The rotor 2B is connected to the outer peripheral surface of the first shaft portion 21, and the rotor 2B and the first shaft portion 21 rotate integrally. The second shaft portion 22 is inserted into the end of the first shaft portion 21 on the engine side in the axial direction. The first shaft portion 21 and the second shaft portion 22 are connected by, for example, spline fitting so as to be integrally rotatable.

  In this specification, unless otherwise specified, “radial direction” indicates a direction orthogonal to the central axis X of the MG shaft 20, and “axial direction” is a direction parallel to the central axis X of the MG shaft 20. It shall be shown.

  The first shaft portion 21 and the second shaft portion 22 are rotatably supported by the case 1 via bearings 3 (first bearing 3A, second bearing 3B, third bearing 3C, and fourth bearing 3D), respectively. . The first shaft portion 21 is supported by the first bearing 3A and the second bearing 3B. The first bearing 3A is disposed on the opposite side of the rotor 2B from the axial engine side, and the second bearing 3B is disposed on the axial engine side (right side in FIG. 1) of the rotor 2B. The second shaft portion 22 is supported by the third bearing 3C and the fourth bearing 3D. The third bearing 3 </ b> C is disposed on the opposite side of the second shaft portion 22 from the axial engine side, and the fourth bearing 3 </ b> D is disposed on the axial end side of the second shaft portion 22 on the engine side.

  The first bearing 3 </ b> A is, for example, a ball bearing, and includes an outer ring 31, an inner ring 32, and a rolling element 33. The outer ring 31 of the first bearing 3A is fitted to the end cover 1A of the case 1, and is press-fitted into the end cover 1A in this embodiment. The end cover 1A closes an opening formed at the end of the case 1 opposite to the engine side in the axial direction, and in the axial direction of the shaft end 20A opposite to the engine side of the MG shaft 20 in the axial direction. Opposite. The outer ring 31 is supported by the case 1 by being press-fitted into the end cover 1A, and the rotation is restricted.

  The inner ring 32 of the first bearing 3A is disposed on the shaft end 20A opposite to the engine side in the first shaft portion 21 (MG shaft 20), and is fitted to the outer periphery of the shaft end 20A by a clearance fit. Yes. The inner ring 32 rotates integrally with the first shaft portion 21. A plurality of rolling elements 33 are continuously arranged in the circumferential direction between the outer ring 31 and the inner ring 32. The rolling element 33 has, for example, a spherical shape, and supports the inner ring 32 rotatably by rolling between the outer ring 31 and the inner ring 32, and enables the first shaft portion 21 to rotate relative to the case 1.

  The second bearing 3B, the third bearing 3C, and the fourth bearing 3D are also ball bearings similar to the first bearing 3A, and are an outer ring fitted to the case 1, an inner ring fitted to the MG shaft 20, and an outer ring. And a rolling element interposed between the inner ring and the inner ring.

  The second shaft portion 22 has a reduction gear 9. The reduction gear 9 is disposed on the outer periphery of the second shaft portion 22 and meshes with the counter driven gear 7 of the counter shaft 6. The reduction gear 9 is disposed between the third bearing 4C and the fourth bearing 3D in the axial direction. The reduction gear 9 is a gear that transmits power input / output to / from the MG shaft 20, that is, power input / output to / from the output shaft of the motor 2.

  The motor 2 can transmit power to the counter shaft 6 via the MG shaft 20, the reduction gear 9 and the counter driven gear 7. In this manner, the reduction driven gear 9 and the counter drive gear of the input shaft are engaged with the counter driven gear 7, and the engine power and the power of the motor 2 are input to the counter shaft 6, respectively. The power input to the countershaft 6 is transmitted to the drive wheels via the final drive gear 8, a ring gear (not shown), a differential mechanism, and an output shaft.

  A generator is connected to the input shaft. In the generator, the input shaft is coaxially arranged, and is connected to the input shaft via, for example, a planetary gear mechanism. The generator can generate electric power by power transmitted through the planetary gear mechanism. Similar to the motor 2, this generator is a motor generator that can also function as an electric motor by electric power supplied from a battery. As described above, the transaxle 100 is a power transmission device for a multi-shaft hybrid vehicle in which two motor generators (motor 2, generator) are arranged on different shafts.

  The bearing lubrication device 5 according to the present embodiment is applied to the MG shaft 20 of the plurality of shafts in such a multi-shaft type trans-ask 100. For this reason, FIG. 1 shows a configuration centering on the MG shaft 20 of the transaxle 100. The bearing lubrication device 5 according to the present embodiment includes an oil passage 4, a guide member 51 (first guide 51A and second guide 51B), an outer edge portion 53, and the like, which will be described later.

  The MG shaft 20 is formed with an oil passage 4 for supplying lubricating oil (oil) to the motor 2 and each bearing 3. The oil passage 4 is a lubricating oil passage that penetrates the MG shaft 20 in the axial direction. The oil passage 4 includes a first oil passage 41 that penetrates the first shaft portion 21 in the axial direction and a second oil passage 42 that penetrates the second shaft portion 22 in the axial direction. The first oil passage 41 and the second oil passage 42 communicate with each other. Lubricating oil is supplied from a catch tank 10 disposed in the case 1 to the shaft end portion on the engine side in the oil passage 4. The catch tank 10 is an oil receiver that can temporarily store lubricating oil. The catch tank 10 is disposed in the upper part in the case 1. Lubricating oil stored in the lower part of the case 1 is sent to the catch tank 10 by rotation of the ring gear or the like.

  The lubricating oil stored in the catch tank 10 is supplied to each part of the transaxle 100 via an oil passage (not shown). The lubricating oil in the catch tank 10 is supplied to the vicinity of the shaft end 20B on the engine side of the MG shaft 20 through an oil passage or the like (indicated by an arrow in FIG. 1). The lubricating oil supplied from the catch tank 10 flows into the oil passage 4 from the axial end 20B on the engine side in the axial direction of the MG shaft 20, and flows in the axial direction toward the first bearing 3A. Then, the MG shaft 20 is discharged in the radial direction while receiving a centrifugal force due to the rotation of the MG shaft 20 from the discharge port 43 of the shaft end 20A opposite to the engine side in the axial direction, and is lubricated to the first bearing 3A. Oil is supplied.

  The MG shaft 20 is formed with a plurality of through holes that communicate the oil passage 4 and the outside of the MG shaft 20 in the radial direction, and the lubricating oil flowing in the MG shaft 20 passes through these through holes. It is supplied to each bearing 3 and the rotor 2B of the motor 2. For example, the second shaft portion 22 is provided with a through hole 44 that communicates from the second oil passage 42 to the space between the second bearing 3 </ b> B and the third bearing 3 </ b> C. Then, the lubricating oil is supplied to the second bearing 3B and the third bearing 3C.

  Here, conventionally, when the gap between the MG shaft 20 and the inner ring of the bearing 3 is fitted, the outer circumference of the MG shaft 20 and the inner ring of the inner ring are increased by, for example, high rotation of the motor 2, unbalance, engine vibration input, torque input, or the like. On the contact surface (contact portion) with the inner periphery, there is a possibility that fretting wear occurs due to the load in the radial direction, the occurrence of sliding, or sliding. As described above, also in the present embodiment, the inner ring 32 of the first bearing 3A and the MG shaft 20 are fitted by clearance fitting.

  In addition, since it is difficult for oil to enter between the MG shaft 20 and the bearing 3, wear may be promoted. Further, when the motor 2 is rotated at a high speed for downsizing and cost reduction, the input becomes larger, and the wear becomes more likely to occur under more severe conditions.

  Therefore, in this embodiment, in order to supply a sufficient amount of lubricating oil to the first bearing 3A, a portion of the inner surface of the case 1 that faces the discharge port 43 of the MG shaft 20, specifically, the inner surface of the end cover 1A. A guide member 51 having a protruding shape (or a wall shape or the like) is provided on the MG shaft 20 side, and guides the lubricating oil (oil) discharged from the discharge port 43 to the first bearing 3A. In addition, the oil can easily enter the contact portion between the MG shaft 20 and the bearing 3.

  The guide member 51 is disposed in a substantially annular shape or concentric shape along the circumferential direction of the MG shaft 20 at a position radially outward from the discharge port 43 of the MG shaft 20. The cross-sectional shape of the guide member 51 along the axis X is a convex shape from the case 1 side toward the discharge port 43 of the MG shaft 20, and has a bottom on the end cover 1A as shown in FIGS. It is triangular.

  Moreover, the guide member 51 has the reflective surface 52 arrange | positioned toward radial inside. In other words, the reflecting surface 52 is arranged such that the normal line intersects the central axis X of the MG shaft 20. The reflecting surface 52 can receive the oil discharged from the discharge port 43 radially outward. And the guide member 51 can be supplied to the 1st bearing 3A by bouncing back the oil received by the reflective surface 52, and scattering oil toward the 1st bearing 3A.

  Here, the guide member 51 can change the portion of the first bearing 3 </ b> A that mainly scatters oil by changing the radial position (radius) of the reflecting surface 52 from the central axis X. In the present embodiment, the radial position from the central axis X of the ridgeline of the guide member 51 (in other words, the upper end of the reflecting surface 52 or the apex on the MG shaft 20 side in the triangular cross section shown in FIG. 2) As the radius of the guide member 51, the guide member 51 has two first guides 51A and second guides 51B having different radii from the central axis X.

  The first guide 51A rebounds the oil discharged from the oil passage 4 toward the radially outer side of the MG shaft 20 toward the contact portion between the inner ring 32 of the first bearing 3A and the MG shaft 20, and the contact portion The radial distance from the central axis X is adjusted so that the oil can be scattered and supplied. The second guide 51B rebounds the oil discharged from the oil passage 4 toward the radially outer side of the MG shaft 20 toward the rolling element 33 of the first bearing 3A, and scatters and supplies the oil to the rolling element 33. The radial distance from the central axis X is adjusted so that

  The radial positional relationship between the first guide 51A and the second guide 51B is such that the radius of the first guide 51A is r1 and the radius of the second guide 51B is r2, and the inner ring 32 of the first bearing 3A and the MG shaft 20 are Since the radial position of the contact portion is radially inward from the radial position of the rolling element 33 of the first bearing 3A, r1 <r2 as shown in FIG. That is, the first guide 51A is always arranged radially inward from the second guide 51B. Further, the first guides 51 </ b> A and the second guides 51 </ b> B are alternately arranged along the circumferential direction around the central axis X of the MG shaft 20.

  More specifically, the guide member 51 has a shape as shown in FIG. 3 when viewed in the direction of the central axis X (viewed in the axial direction). In FIG. 3, the locus of the ridgeline of the guide member 51 in the axial direction view is shown by a solid line. As shown in FIG. 3, in the present embodiment, the locus of the ridgeline of the guide member 51 is such that the minimum value of the distance from the central axis X is the radius r1 of the first guide 51A, and the maximum value is the radius r2 of the second guide 51B. And the waveform is continuously connected between them.

  In such a guide member 51, when the oil discharged from the discharge port 43 of the MG shaft 20 collides with the reflecting surface 52A of the first guide 51A at the position of the radius r1, as shown by a broken line A in FIG. In addition, the oil bounced off the reflecting surface 52 </ b> A is scattered around the contact portion between the inner ring 32 of the first bearing 3 </ b> A and the MG shaft 20. On the other hand, when the oil discharged from the discharge port 43 of the MG shaft 20 collides with the reflection surface 52B of the second guide 51B at the position of the radius r2, as shown by the broken line B in FIG. The bounced oil is scattered around the rolling elements 33 of the first bearing 3A.

  In addition, the part which connects between the 1st guide 51A and the 2nd guide 51B shown with a broken line in FIG. 3 functions as the intermediate guide 51C which has the intermediate | middle role of the 1st guide 51A and the 2nd guide 51B. . That is, the intermediate guide 51C scatters oil at an intermediate position between the oil supply location (the contact portion between the inner ring 32 and the MG shaft 20) by the first guide 51A and the oil supply location (the rolling element 33) by the second guide 51B. Can be made. For example, the centrifugal force applied to the oil discharged from the discharge port 43 is changed due to a change in the vehicle speed (the number of rotations of the MG shaft 20), and the oil supply positions by the first guide 51A and the second guide 51B are slightly shifted. Even so, the intermediate guide 51C of the guide member 51 can supply oil to the contact portion between the inner ring 32 and the MG shaft 20 and the rolling element 33 instead.

  Furthermore, in the present embodiment, the discharge port 43 of the oil passage 4 is provided with an outer edge portion 53 that protrudes in the axial direction from the shaft end portion 20 </ b> A of the MG shaft 20. The outer edge portion 53 has a cylindrical shape along the inner peripheral surface of the oil passage 4. The outer edge portion 53 and the reflecting surface 52 of the guide member 51 are at least partially overlapped (overlapped) in the axial direction. In other words, the axial position of the protruding end of the outer edge 53 is closer to the case 1 than the position of the convex ridgeline of the guide member 51. By providing such an outer edge portion 53, the oil is discharged radially outward through the outer edge portion 53, so that the oil reliably collides with the reflecting surface 52 of the guide member 51, and the first bearing 3A to be lubricated. The oil can be reliably supplied.

  As described above, the bearing lubrication device 5 according to the present embodiment includes the oil passage 4 formed so that oil can be discharged from the inside of the MG shaft 20 to the radially outer side, and the oil passage 4 to the radially outer side of the MG shaft 20. The oil discharged toward the contact portion between the inner ring 32 of the first bearing 3A and the MG shaft 20 is bounced back and scattered, and the oil is supplied to the contact portion from the first guide 51A and the oil passage 4 to the MG. A second guide 51 </ b> B that repels the oil discharged toward the radially outer side of the shaft 20 toward the rolling element 33 of the first bearing 3 </ b> A and scatters the oil, and supplies the oil to the rolling element 33. . The first guide 51 </ b> A and the second guide 51 </ b> B are arranged along the circumferential direction around the central axis X of the MG shaft 20.

  With such a configuration, the first guide 51A mainly supplies oil to the contact portion between the inner ring 32 of the first bearing 3A and the MG shaft 20, so that the gap between the first bearing 3A and the MG shaft 20 is provided. Oil can enter easily. Further, since the second guide 51B concentrates oil on the rolling elements 33 of the first bearing 3A, the rolling elements 33 can be sufficiently lubricated. Therefore, wear of the first bearing 3A can be suitably suppressed.

  Furthermore, since both the first guide 51A and the second guide 51B are configured to rebound the oil once discharged from the oil passage 4 in the MG shaft 20 and scatter the oil, inevitably from the MG shaft 20 and the first bearing 3A. Since it is arranged at a separated position and there is no need to form a guide path on the MG shaft 20 in order to supply oil to the gap between the first bearing 3A and the MG shaft 20 as in the prior art, the MG shaft 20 The strength of can be secured.

  As a result, the strength of the MG shaft 20 can be ensured while suppressing wear of the first bearing 3A. Further, the oil is scattered in the direction of the rolling element 33 of the first bearing 3A, and the amount of oil penetrating the first bearing 3A can be increased, and the oil staying in the vicinity of the first bearing 3A is reduced. Stirring loss can be reduced.

(First modification of the first embodiment)
In this embodiment, the shape of the guide member 51 as viewed in the axial direction is a waveform that changes continuously with the first guide 51A as the minimum value of the radial position and the second guide 51B as the maximum value. The first guide 51A and the second guide 51B having the radius r2 need only be arranged along the circumferential direction around the central axis X of the MG shaft 20. For example, the shape shown in FIG.

  The shape of the guide member 51 shown in FIG. 4 includes a first guide 51A in which the radius of the ridge line is r1, a second guide 51B in which the radius of the ridge line is r2, and an intermediate guide in which the radius of the ridge line is between r1 and r2. 51C is a shape that is intermittently arranged in a concentric manner around the central axis X.

  In the example illustrated in FIG. 4, the intermediate guide 51 </ b> C includes two types having different radii, but the intermediate guide may be provided with one or a plurality of other types. In the example of FIG. 4, the first guide 51A, the intermediate guide 51C, and the second guide 51B are periodically arranged in the radial order, but the arrangement order of the guides may be arbitrary. Moreover, it is preferable that the installation number of the first guide 51A, the intermediate guide 51C, and the second guide 51B is substantially the same.

(Second modification of the first embodiment)
Similarly, as shown in FIG. 5, the shape of the guide member 51 in the axial direction is such that the first guide 51 </ b> A having the ridge radius r <b> 1 is arranged in the majority of the guide member 51, and the radius of the ridge line is locally localized. It is also possible to arrange the second guide 51B with r2 and connect the first guide 51A and the second guide 51B continuously and use this connection portion as the intermediate guide 51C.

(Third Modification of First Embodiment)
Further, as shown in FIG. 6, the shape of the guide member 51 in the axial direction is opposite to the second modification example, in which the second guide 51B having a ridge line radius r2 is arranged in the majority of the guide member 51, A configuration in which a first guide 51A having a ridge radius r1 is disposed in a local part, the first guide 51A and the second guide 51B are continuously connected, and this connection portion is used as an intermediate guide 51C. It can also be.

(Fourth modification of the first embodiment)
Further, as shown in FIG. 7, the shape of the guide member 51 viewed in the axial direction is configured as an elliptical shape in which the first guide 51A having the radius r1 has a short diameter and the second guide 51B having the radius r2 has a long diameter. You can also. In this case, a portion between the major axis and the minor axis of the elliptical shape becomes the intermediate guide 51C.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 8 is a diagram showing a configuration of a bearing lubrication device 15 according to the second embodiment of the present invention.

  As shown in FIG. 8, in the bearing lubrication device 15 according to the present embodiment, the radius r1 of the first guide 151A of the guide member 151 and the radius r2 of the second guide 151B are the same (r1 = r2). The present embodiment is different from the bearing lubrication device 5 of the first embodiment in that the inclination angle of the reflecting surface 152 is changed between the first guide 151A and the second guide 151B.

  As shown in FIG. 8, the inclination angle of the reflecting surface 152B of the second guide 151B is set to be looser than that of the reflecting surface 152A of the first guide 151A. Therefore, the oil discharged from the discharge port 43 of the MG shaft 20 and colliding with the reflecting surface 152B of the second guide 151B from the radially inner side is directed more radially outward than the case of the reflecting surface 152A of the first guide 151A. Bounced back. That is, the oil supply position to the first bearing 3A by the reflecting surface 152B of the second guide 151B can be farther from the central axis X than in the case of the first guide 151A.

  In the present embodiment, the first guide 151A is configured such that the oil discharged from the oil passage 4 toward the radially outer side of the MG shaft 20 and the inner ring 32 of the first bearing 3A and the MG shaft, as indicated by a broken line A in FIG. The angle of inclination of the reflecting surface 152A is adjusted so that oil can splash and be supplied to the contact portion. As shown by a broken line B in FIG. 8, the second guide 151B rebounds the oil discharged from the oil passage 4 toward the radially outer side of the MG shaft 20 toward the rolling element 33 of the first bearing 3A, The inclination angle of the reflecting surface 152B is adjusted so that oil can be scattered and supplied to the moving body 33.

  Note that the shape of the guide member 151 viewed in the axial direction may be a plurality of patterns similar to those of the first embodiment illustrated in FIGS. 3 to 7, but in this embodiment, the lower end of the reflecting surface 152 (see FIG. In the cross-sectional shape shown, the locus of the position 153 (intersection with the end cover 1A) corresponds to the locus of the ridge line illustrated in FIGS. The radial position of the lower end 153A of the reflecting surface 152A of the first guide 151A corresponds to the maximum value (r2) of the locus of the ridge line exemplified in FIGS. 3 to 7, and the diameter of the lower end 153B of the reflecting surface 152B of the second guide 151B. The direction position corresponds to the minimum value (r1) of the locus of the ridgeline exemplified in FIGS.

  As mentioned above, although preferred embodiment was shown and demonstrated about this invention, this invention is not limited by these embodiment. For example, in the above embodiment, the structure for lubricating the first bearing 3 </ b> A provided at the end of the MG shaft 20 has been described. However, the bearing lubrication device according to the present invention is an intermediate portion other than the end of the MG shaft 20. It is also applicable to lubrication of the second bearing 3B and the third bearing 3C supported by For example, as shown in FIG. 9, oil discharged from the oil passage 4 in the MG shaft 20 through the through hole 44 to the space between the second bearing 3B and the third bearing 3C A guide member 251 for guiding toward the three bearings 3C can be provided. The guide member 251 can be fixed to the case 1 facing between the second bearing 3B and the third bearing 3C.

  The guide member 251 has a reflective surface 252 that repels oil discharged radially outward from the through hole 44 in the direction of the second bearing 3B and the third bearing 3C. Further, the guide member 251 includes two first guides 251A and second guides 251B in which the position of the reflection surface 252 from the central axis X is different, like the guide member 51 of the first embodiment.

  As shown by a broken line A ′ in FIG. 9, the first guide 251 </ b> A allows oil discharged radially outward from the through hole 44 between the inner rings of the second bearing 3 </ b> B and the third bearing 3 </ b> C and the MG shaft 20. The position of the reflecting surface 252A from the central axis X is adjusted so that oil can be scattered and supplied to the contact portion by splashing back toward the contact portion. As shown by a broken line B ′ in FIG. 9, the second guide 251 </ b> B repels oil discharged radially outward from the through hole 44 toward the rolling elements of the second bearing 3 </ b> B and the third bearing 3 </ b> C. The position of the reflection surface 252B from the central axis X is adjusted so that oil can be scattered and supplied to the rolling elements.

  Although not shown in FIG. 9, as with the guide member 151 of the second embodiment, the position of the reflecting surface 252 is made the same, and the tilt angle of the reflecting surface 252 is changed to change the oil supply position. A configuration is also possible.

  In the above-described embodiment, the configuration in which the bearing lubrication devices 5 and 15 according to the present invention are applied to the MG shaft 20 that is the rotation shaft of the motor 2 of the hybrid vehicle is illustrated. For example, other shafts (input shaft, countershaft 6 and output shaft) of a transaxle 100 of a hybrid vehicle, an EV (electric vehicle), and a gasoline vehicle can be applied. The present invention can also be applied to a power transmission device (such as AT or CVT).

  Further, the contents disclosed in the above embodiments and modifications can be applied in appropriate combination.

3 Bearing (3A ... 1st bearing, 3B ... 2nd bearing, 3C ... 3rd bearing, 3D ... 4th bearing)
31 Outer ring 32 Inner ring 33 Rolling element 20 MG shaft 4 Oil passage 5, 15 Bearing lubrication device 51, 151, 251 Guide member 51A, 151A, 251A First guide 51B, 151B, 251B Second guide 52, 152, 252 Reflecting surface

Claims (3)

A bearing lubrication device for lubricating a bearing supporting a shaft,
An oil passage formed so that oil can be discharged radially outward from the inside of the shaft end of the shaft;
The oil discharged from the oil passage toward the outer side in the radial direction of the shaft is rebounded and scattered toward the contact portion between the inner ring of the bearing and the shaft, and the oil is supplied to the contact portion. 1 guide,
A second guide that repels and disperses the oil discharged from the oil passage toward the radially outer side of the shaft toward the rolling element of the bearing, and supplies the oil to the rolling element;
With
The first guide and the second guide are arranged along a circumferential direction around the shaft center of the shaft , and have a protruding portion that stands up against the oil flow. Lubrication equipment.   2. The bearing lubrication device according to claim 1, wherein the first guide and the second guide have different radial positions from the shaft center of the shaft.   3. The bearing lubrication device according to claim 1, wherein the first guide and the second guide have different angles of inclination of reflecting surfaces that bounce off the oil discharged from the oil passage. 4.

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