JP2017145900A - transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To smoothly lubricate a connection/disconnection mechanism by supplying lubricating oil directly to the connection/disconnection mechanism adjacent to a planetary gear mechanism.SOLUTION: A transmission has: a planetary gear mechanism (10) which is provided with a sun gear (11) arranged in a rotating shaft (61), a plurality of pinion gears (12), a carrier (13) supporting a plurality of pinion gears (12), and a ring gear (15) engaged with a ring gear (12) on the outer diameter side of the carrier (13); a connection/disconnection mechanism (80) connecting/disconnecting the planetary gear mechanism (10); an operation member (90) operating the connection/disconnection mechanism (80); a case (51) of the transmission housing the planetary gear mechanism (10), the disconnection mechanism (80), and the operation member (90); and an attachment member (20) for attaching the ring gear (15) of the planetary gear mechanism (10) to the case (51). In the mounting member (20), an opening (21) for introducing a lubricating oil is formed above the operation member (90).SELECTED DRAWING: Figure 2

Description

  The present invention relates to a transmission including a planetary gear mechanism that transmits a driving force from a driving source.

  Conventionally, there is a transmission having a planetary gear mechanism (planetary gear mechanism) having a sun gear, a pinion gear, and a ring gear (see, for example, Patent Document 1). In the planetary gear mechanism, there is an external gear sun gear at the center, and a plurality of small external gear pinion gears mesh with each other at equal intervals. The outside of the pinion gear meshes with a ring gear that is an internal gear. The rotation shaft of the pinion gear is attached to a frame called a carrier. With this configuration, the planetary gear mechanism can change the driving direction and the gear ratio by inputting / outputting and fixing the rotation shafts of the three gears of the sun gear, the pinion gear, and the ring gear.

  By the way, when changing the gear ratio in the planetary gear mechanism, the gear ratio conversion is performed by operating a connecting / disconnecting mechanism such as an adjacent synchromesh mechanism. For this reason, it is necessary to lubricate the connection / disconnection mechanism.

  However, when there is a motor (electric motor) in the outer diameter direction of the planetary gear mechanism as in Patent Document 1, it is difficult to supply the lubricating oil directly to the connection / disconnection mechanism adjacent to the planetary gear mechanism.

Japanese Patent Laying-Open No. 2015-175463

  The present invention has been made in view of the above-described points, and an object of the present invention is to smoothly lubricate the connecting / disconnecting mechanism by supplying lubricating oil directly to the connecting / disconnecting mechanism adjacent to the planetary gear mechanism. Is to provide a simple transmission.

  In order to solve the above problems, a transmission (50) according to the present invention includes a sun gear (11) disposed on a rotating shaft (61) and a plurality of pinion gears (12) meshing with the outer diameter side of the sun gear (11). A planetary gear mechanism (10) comprising: a carrier (13) that supports a plurality of pinion gears (12); and a ring gear (15) that meshes with the pinion gear (12) on the outer diameter side of the carrier (13); Connection / disconnection mechanism (80) for connecting / disconnecting planetary gear mechanism (10), operation member (90) for operating connection / disconnection mechanism (80), planetary gear mechanism (10), connection / disconnection mechanism (80) and operation A transmission case (51) for housing the member (90), and an attachment member (20) for attaching the ring gear (15) of the planetary gear mechanism (10) to the case (51). 20), the operation member (90 Above the, characterized in that the opening for introducing the lubricating oil (21) is formed.

  Thus, in the attachment member (20) for attaching the planetary gear mechanism (10) to the case (51), the transmission (50) is formed by forming the opening (21) above the operation member (90). Lubricating oil scattered inside enters from the opening (21) of the mounting member (20) by free fall. And since the opening part (21) is formed above the operation member (90), lubricating oil is supplied to the operation member (90). Thereby, lubrication of the connecting / disconnecting mechanism (80) can be performed smoothly by supplying lubricating oil directly to the operating member (90) of the connecting / disconnecting mechanism (80) adjacent to the planetary gear mechanism (10). it can.

  In the transmission (50), an electric motor (40) is disposed on the outer periphery of the ring gear (15), and the opening (21) is an axial end of the electric motor (40) and the electric motor (40). ) In the radial direction. With such a configuration, the lubricating oil supplied or scattered to the electric motor (40) can fall along the axial end of the electric motor (40) to the opening (21). For this reason, lubricating oil can be efficiently and reliably supplied to the operating member (90).

  In the transmission (50), the opening (21) may have an inclined surface (22) formed so that the opening area increases as it goes upward. Thus, when it is the structure which has the inclined surface (22) from which an opening area becomes large as an opening part (21) goes upwards, more lubricating oil supplied below by free fall will have an opening part ( 21) and the area of the opening becomes smaller as it goes downward, so that it is possible to reliably supply the lubricating oil to a location where lubrication is desired. Therefore, the lubricating oil can be reliably supplied to the operation member (90).

  In the transmission (50), the portion where the opening (21) is formed may be a portion where a fixing member (20B) for fixing the attachment member (20) to the case (51) is disposed. . Thus, if the part which forms an opening part (21) is made to correspond with the part by which a fixing member (20B) is arrange | positioned, arrangement | positioning of an opening part (21) can be performed efficiently and space saving can be achieved. it can. In other words, the portion where the fixing member (20B) for fixing the mounting member (20) to the case (51) is disposed originally needs to be formed in a recessed shape. If an opening is formed in this recessed portion to form the opening (21), in addition to the process of recessing a part of the attachment member (20) to dispose the fixing member (20B), the attachment member ( 20) It is no longer necessary to perform a special process for recessing. Thereby, arrangement | positioning of an opening part (21) can be performed efficiently.

  In the transmission (50), the case (51) may be formed with an inclined portion (51A) for guiding the lubricating oil to the opening (21). Thus, when the inclined portion (51A) is formed in the case (51) and the lubricating oil is guided to the opening (21) through the inclined portion (51A), the transmission (50) Lubricating oil supplied or scattered around the mounting member (20) can be effectively supplied to the opening (21) through the inclined portion (51A). Therefore, the lubricating oil can be reliably supplied to the operation member (90).

In the transmission (50), an oil pump (55) that feeds lubricating oil to the transmission (50) and a planetary gear mechanism (10) that supplies the lubricating oil from the oil pump (55) to the case (51). A lubricating oil pipe (56) that guides to () is disposed, and a discharge port (56H) may be formed in the lubricating oil pipe (56) above the inclined portion (51A). As described above, when the discharge port (56H) is provided in the lubricant pipe (56) through which the lubricant passes, the lubricant is dripped from the discharge port (56H). Since the discharge port (56H) is formed above the inclined portion (51A), the lubricating oil dropped from the discharge port (56H) is guided to the opening (21) through the inclined portion (51A). The Thereby, the lubricating oil dripped from the lubricating oil pipe (56) can be effectively used for lubricating the planetary gear mechanism (10).
In addition, the code | symbol in said parenthesis has shown the code | symbol of the corresponding component of embodiment mentioned later as an example of this invention.

  According to the transmission of the present invention, the connection / disconnection mechanism can be smoothly lubricated by supplying lubricating oil directly to the connection / disconnection mechanism.

It is a skeleton figure of a transmission using a planetary gear mechanism. It is an axial sectional view showing the periphery of the planetary gear mechanism partially enlarged. It is a perspective view which shows the detailed structure of the upper part of an attachment member. It is the side view to which the peripheral part of the fixing member was expanded.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. First, the overall configuration of the transmission 50 using the planetary gear mechanism 10 (planetary gear mechanism) as a drive transmission unit will be described. FIG. 1 is a skeleton diagram of a transmission 50 using the planetary gear mechanism 10. The transmission 50 shown in FIG. 1 is a parallel shaft transmission of 7 forward speeds and 1 reverse speed, and is a dry dual clutch transmission (DCT).

  The transmission 50 includes a first input shaft 61 (rotary shaft) coupled to an internal combustion engine (not shown) via a first clutch C1 for odd-numbered stages and a second clutch C2 for even-numbered stages. The second input shaft 62 coupled to the internal combustion engine via the first input shaft 61 and the second input shaft 62 is connected to the internal combustion engine so as to be connectable / disconnectable, and corresponds to the selected gear stage. And a planetary gear mechanism 10 provided on one end side of the first input shaft 61. Further, a rotor 41 (rotor) of the electric motor 40 is fixed to one end of the first input shaft 61 so as to rotate integrally with a stator 42 (stator) of the electric motor 40, and the internal combustion engine and the electric motor 40 are driven as a drive source. It functions as a transmission of a hybrid vehicle. The counter shaft 63 is coupled to a differential mechanism (not shown) and drives the driving wheel of the vehicle.

  The features of the present invention are related to the peripheral structure of the planetary gear mechanism 10, and other known transmission gear mechanisms may appropriately use known configurations. However, in order to understand the outline of the embodiment, first, the transmission gear mechanism of the transmission 50 other than the planetary gear mechanism 10 will be outlined, and then the explanation related to the planetary gear mechanism 10 will be given.

  An outer main shaft OMS is connected to the output side of the second clutch C <b> 2, and the outer main shaft OMS is arranged concentrically so as to form an outer cylinder of the first input shaft 61. The outer main shaft OMS is always engaged with the reverse shaft RVS and the second input shaft 62 via the idle shaft IDS, and the rotation output of the second clutch C2 is transmitted to the reverse shaft RVS and the second input shaft 62. Each axis is parallel to each other.

  On the 1st input shaft 61, the 3rd speed drive gear 73, the 7th speed drive gear 77, and the 5th speed drive gear 75 are each arrange | positioned concentrically so that relative rotation is possible. A 3-7 speed synchromesh mechanism 81 is slidably provided in the axial direction between the 3rd speed drive gear 73 and the 7th speed drive gear 77, and a 5th speed synchromesh mechanism 83 corresponding to the 5th speed drive gear 75 is provided. Is slidable in the axial direction.

  The gear stage is connected to the first input shaft 61 by sliding the synchromesh mechanism corresponding to the desired gear stage to put the gear stage in sync. These gears and the synchromesh mechanism provided in association with the first input shaft 61 constitute a first transmission gear mechanism for realizing odd-numbered gear stages (3, 5, 7th speed).

  Each drive gear of the first transmission gear mechanism meshes with a corresponding gear among driven gears provided on the counter shaft 63. Specifically, the third speed drive gear 73 is engaged with the first driven gear 91, the seventh speed drive gear 77 is engaged with the second driven gear 92, and the fifth speed drive gear 75 is engaged with the third driven gear 93. By engaging in this way, the counter shaft 63 is rotationally driven.

  Similarly, a second speed drive gear 72, a sixth speed drive gear 76, and a fourth speed drive gear 74 are concentrically disposed on the second input shaft 62 so as to be relatively rotatable. A 2-6 speed synchromesh mechanism 82 is slidably provided in the axial direction between the 2nd speed drive gear 72 and the 6th speed drive gear 76, and a 4th speed synchromesh mechanism 84 corresponding to the 4th speed drive gear 74 is provided. Is slidable in the axial direction.

  The gear stage is connected to the second input shaft 62 by sliding the synchromesh mechanism corresponding to the desired gear stage to put the gear stage in sync. These gears and the synchromesh mechanism provided in association with the second input shaft 62 constitute a second transmission gear mechanism for realizing even-numbered gear stages (2, 4, and 6 speeds).

  Each drive gear of the second transmission gear mechanism meshes with a corresponding gear among driven gears provided on the counter shaft 63. Specifically, the second speed drive gear 72 is engaged with the first driven gear 91, the sixth speed drive gear 76 is engaged with the second driven gear 92, and the fourth speed drive gear 74 is engaged with the third driven gear 93. By engaging in this way, the counter shaft 63 is rotationally driven.

  The planetary gear mechanism 10 is disposed at one end of the first input shaft 61 near the electric motor 40. The planetary gear mechanism 10 includes a sun gear 11, a pinion gear 12, and a ring gear 15. The sun gear 11 is fixed to the first input shaft 61 and rotates integrally with the first input shaft 61 and the electric motor 40. The ring gear 15 is fixed to the case 51 of the transmission 50 via the mounting member 20 and is configured to generate a shift output from the carrier 13 of the pinion gear 12. A first-speed synchromesh mechanism 80 is provided between the carrier 13 and the third-speed drive gear 73 on the first input shaft 61.

  The first speed synchromesh mechanism 80 is turned on according to the selection of the first speed gear stage, whereby the carrier 13 and the third speed drive gear 73 on the first input shaft 61 are connected. Then, the rotation of the carrier 13 is transmitted to the gear 73 and the counter shaft 63 is rotationally driven via the first driven gear 91. As a result, the rotation of the first input shaft 61 is shifted at a first gear ratio determined by the combination of the gear ratio of the planetary gear mechanism 10 and the gear ratio of the third speed drive gear 73, and the final output shaft is transmitted via the counter shaft 63. (Not shown).

  At this time, since the 3-7 speed synchromesh mechanism 81 is in the neutral position, the 3-7 speed synchromesh mechanism 81 is not engaged with the 3rd speed drive gear 73. When the second to seventh speeds higher than the first speed are selected, the first speed synchromesh mechanism 80 is off and the carrier 13 and the third speed drive gear 73, that is, the counter shaft 63 are not connected.

  As described above, the synchromesh mechanism 80 is provided so as to be able to be connected to and disconnected from the carrier 13 in order to select a predetermined gear position, and is configured to transmit the rotation of the carrier 13 to the counter shaft 63 when connected. , Function as a binding element. Such a coupling element may use a configuration other than the synchromesh mechanism as long as an equivalent function can be realized.

  In the present embodiment, in the planetary gear mechanism 10, when the ring gear 15 is always fixed and a predetermined gear (for example, first speed) is selected, the rotation of the carrier 13 passes through the synchromesh mechanism 80 via the third speed drive gear 73. This is a configuration that is transmitted to the counter shaft 63. When a gear other than the predetermined gear is selected, the carrier 13 is disconnected from the third-speed drive gear 73, so that the carrier 13 does not always rotate with the counter shaft 63, and the first input shaft It only rotates according to the rotation of the sun gear 11 according to the rotation of 61.

  Moreover, since the ring gear 15 is always fixed, it does not rotate. Thus, since the carrier 13 does not rotate with the counter shaft 63, the differential rotation of the planetary gear mechanism 10 can be suppressed particularly in a high vehicle speed range where the work load is large. For this reason, no-load rotation loss can be greatly reduced, and heat generation due to rotational friction can be suppressed. Accordingly, the power transmission efficiency of the transmission 50 is improved, and the fuel consumption and the cooling performance are also improved.

  Next, the reverse axis RVS will be described. A gear 97 that engages with the idle shaft IDS is fixed to the reverse shaft RVS. Further, a reverse gear stage for selectively coupling the reverse shaft RVS to the first input shaft 61 is provided on the outer periphery of the reverse shaft RVS.

  The reverse gear stage includes a reverse drive gear 98 that is concentrically provided so as to be rotatable relative to the reverse shaft RVS, and a reverse synchromesh mechanism 85 for selectively coupling the reverse drive gear 98 to the reverse shaft RVS. , And a gear 78 fixed to the first input shaft 61 so as to mesh with the reverse drive gear 98.

  The reverse synchromesh mechanism 85 is slidable in the axial direction of the reverse axis RVS. Turn off when traveling forward. That is, the reverse shaft RVS is not engaged with the reverse drive gear 98. On the other hand, when the vehicle is traveling backward, it is ON, that is, the reverse shaft RVS is engaged with the reverse drive gear 98.

  The peripheral structure of the planetary gear mechanism 10 and the synchromesh mechanism 80 in the present embodiment will be described. FIG. 2 is an axial cross-sectional view showing the periphery of the planetary gear mechanism 10 partially enlarged. As shown in FIG. 2, the planetary gear mechanism 10 is disposed adjacent to the first-speed synchromesh mechanism 80. In FIG. 2, the first input shaft 61 is shown at the lower end, and the outer diameter side of the electric motor 40 is shown upward. For this reason, in the following description using FIG. 2, “upper” means the outer diameter direction of the first input shaft 61, and conversely, “lower” means the inner diameter direction of the first input shaft 61.

  The first-speed synchromesh mechanism 80 (connection / disconnection mechanism) has a known structure. That is, the synchromesh mechanism 80 includes a synchronizer hub 80A, a synchronizer sleeve 80B that rotates together with the synchronizer hub 80A by spline coupling, and engages with the synchronizer hub 80A so as to be relatively displaceable in the axial direction. And a dog spline portion 80C having a tapered surface frictionally engaged with the tapered friction surface of the synchronizer ring.

  The synchronizer sleeve 80B is moved in the axial direction by the shift fork 90 (operation member) to connect and disconnect the dog spline portion 80C of the synchromesh mechanism 80. That is, the synchronizer sleeve 80B is moved between the portion indicated by the broken line and the portion indicated by the solid line in FIG. 2 by the shift fork 90 that moves in the axial direction.

  The overall configuration of the planetary gear mechanism 10 will be described. The planetary gear mechanism 10 includes a sun gear 11 disposed on the first input shaft 61, a plurality of pinion gears 12 that mesh with the outer diameter side of the sun gear 11, a carrier 13 that supports the plurality of pinion gears 12, and an outer diameter of the carrier 13. A ring gear 15 that meshes with the pinion gear 12 on the side, and an attachment member 20 that retains the outer diameter of the ring gear 15 and attaches the planetary gear mechanism 10 to the case 51 of the transmission 50. Next, each component will be described in detail.

  The sun gear 11 is an external gear disposed in the center of the planetary gear mechanism 10. The sun gear 11 is inserted and fixed in the axial direction at one end of the first input shaft 61, and is assembled so as to rotate integrally with the first input shaft 61. The hub 13 </ b> A of the carrier 13 is supported by the bearing 30 so as to relatively rotate on the outer periphery of the first input shaft 61. A synchronizer hub 80A of the first-speed synchromesh mechanism 80 is assembled to the hub 13A of the carrier 13 so as to rotate integrally.

  The pinion gears 12 are external gears that are uniformly disposed around the sun gear 11 so as to mesh with the sun gear 11. The rotation shaft 12 </ b> A of the pinion gear 12 is attached to a frame called a carrier 13.

  The ring gear 15 is an internal gear that meshes with the pinion gear 12 outside the pinion gear 12. The ring gear 15 is attached to one end of the annular attachment member 20 so as to be spline-engaged. Thereby, the ring gear 15 is fixed so as not to rotate with respect to the mounting member 20, and is fixed to the mounting member 20 so as to be slidable in the axial direction of the first input shaft 61. Further, the ring gear 15 is prevented from being detached from the mounting member 20 by the retaining member 15S.

  Next, the lubricating oil supply structure around the planetary gear mechanism 10 of the transmission 50 will be described. As shown in FIG. 2, an oil pump 55 that feeds lubricating oil to the transmission 50 is disposed inside the case 51 of the transmission 50. Lubricating oil is supplied from the oil pump 55 to the periphery of the electric motor 40 and the planetary gear mechanism 10 to perform lubrication and cooling.

  The oil pump 55 is connected to a lubricating oil pipe 56 that guides the lubricating oil from the oil pump 55. One of the lubricating oil pipes 56 is connected to the oil pump 55, and the other is inserted and connected to the pipe insertion portion 52 of the case 51. A discharge port 56 </ b> H through which a part of the lubricating oil in the lubricating oil pipe 56 is discharged is formed on the inner diameter side in the middle of the lubricating oil pipe 56.

  In the case 51, a lubricating oil guide portion 51 </ b> G that guides the lubricating oil to a position facing the stator 42 is formed at the tip of the pipe insertion portion 52 in which the lubricating oil pipe 56 is inserted. The lubricating oil guide 51G is formed in an annular shape so as to face the end of the cylindrical stator 42 on the case 51 side, and has a plurality of lubricating oil jets 51H. Since FIG. 2 is a cross-sectional view, only one lubricating oil jet 51H is shown.

  In addition, an inclined portion 51 </ b> A is formed below the lubricating oil pipe 56 of the case 51. The inclined portion 51 </ b> A is inclined downward from the position of the oil pump 55 toward the mounting member 20 of the planetary gear mechanism 10. Since the discharge port 56H of the lubricating oil pipe 56 is formed above the inclined portion 51A of the inclined portion 51A, the lubricating oil discharged from the discharge port 56H is guided toward the mounting member 20 through the inclined portion 51A.

  With this lubricating oil supply structure, the lubricating oil supplied from the oil pump 55 is guided to the lubricating oil pipe 56 as indicated by an arrow. A part of the lubricating oil in the lubricating oil pipe 56 moves downward (in the direction D1) from the discharge port 56H, and is guided to the upper portion of the mounting member 20 through the inclined portion 51A. On the other hand, the lubricating oil that has not been discharged from the discharge port 56H moves upward (in the direction D2), travels through the lubricating oil guide portion 51G, and is discharged from the lubricating oil outlet 51H toward the stator 42. Thereafter, the lubricating oil is guided to the upper portion of the mounting member 20 through the end portions of the stator 42 and the rotor 41 which are constituent members of the electric motor 40.

  An opening 21 is formed at the upper end of the attachment member 20. As described above, the opening 21 is disposed at the axial ends of the stator 42 and the rotor 41, which are constituent members of the electric motor 40, and inside the radial direction of the electric motor 40, that is, below the FIG. For this reason, the lubricating oil guided to the mounting member 20 is supplied into the mounting member 20 through the opening 21.

  Here, a detailed configuration of the opening 21 of the mounting member 20 will be described. FIG. 3 is a perspective view showing a detailed configuration of the upper part of the mounting member 20. In FIG. 3, the configurations of the case 51, the electric motor 40, and the planetary gear mechanism 10 are omitted.

  As shown in FIG. 3, the attachment member 20 is formed with an opening 21 for introducing lubricating oil. The opening 21 introduces lubricating oil and supplies the lubricating oil to the planetary gear mechanism 10 disposed below. In particular, since the opening 21 is formed above the shift fork 90 and the synchromesh mechanism 80, the lubricating oil from the opening 21 is effectively supplied to a structure for switching the synchromesh mechanism 80.

  Moreover, although the side surface of the opening 21 is inclined, the inclined surface 22 is formed so that the opening area increases as it goes upward as shown in FIG. Thus, since the opening 21 has the largest opening area at the upper end, more lubricating oil can be easily taken into the mounting member 20. On the other hand, since the opening area is relatively small in the lower part, the lubricating oil can be easily guided to a desired position.

  Further, the portion of the mounting member 20 where the opening 21 is formed is a portion where a fixing member 20B such as a bolt for fixing the mounting member 20 to the case 51 is disposed. The mounting member 20 is a hollow, substantially annular member for fixing the periphery of the ring gear 15 of the planetary gear mechanism 10, but a fixing side surface 23 for disposing the fixing member 20 </ b> B is required for fixing the mounting member 20 to the case 51. is there. In the mounting member 20 of the present embodiment, four fixed side surfaces 23 are formed, but the number is not limited to four.

  FIG. 4 is an enlarged side view of the periphery of the fixing member 20B. FIG. 4 is a view as seen from the direction A in FIG. The fixing member 20B disposed on the fixed side surface 23 is preferably disposed on the inner diameter side of the planetary gear mechanism 10 in order to save space. For this reason, the fixed side surface 23 is formed not to be outside of the outer periphery 24 of the mounting member 20 but to have a part of the fixed side surface 23 in a portion in which a part of the outer periphery 24 is recessed as shown in FIG. In the present embodiment, the recessed portion is effectively used by forming the opening 21 in the portion where the outer periphery 24 is recessed inward to save space.

  As described above, according to the transmission 50 according to the present embodiment, by forming the opening 21 above the shift fork 90 in the mounting member 20 for mounting the planetary gear mechanism 10 to the case 51, the transmission 50 Lubricating oil scattered inside enters from the opening 21 of the mounting member 20 by free fall. Since the opening 21 is formed above the shift fork 90, the lubricating oil that has entered from the opening 21 is reliably supplied to the shift fork 90. Thereby, the synchromesh mechanism 80 can be smoothly lubricated by supplying the lubricating oil directly to the shift fork 90.

  Further, in the transmission 50, the electric motor 40 is disposed on the outer periphery of the ring gear 15, and the opening 21 is arranged at an end portion in the axial direction of the electric motor 40 and inside the radial direction of the electric motor 40. Thereby, the lubricating oil supplied to or scattered from the electric motor 40 can fall along the axial end of the electric motor 40 to the opening 21. For this reason, lubricating oil can be supplied to the shift fork 90 efficiently and reliably.

  In the transmission 50, the opening 21 may have an inclined surface 22 formed so that the opening area increases as it goes upward. Thus, when the opening 21 has the inclined surface 22 whose opening area increases as it goes upward, more of the lubricating oil supplied downward due to free fall enters the opening 21. In addition, since the opening area decreases as it goes downward, the lubricating oil can be reliably supplied to a location where lubrication is desired. Therefore, the lubricating oil can be reliably supplied to the shift fork 90.

  In the transmission 50, the portion where the opening 21 is formed may be a portion where a fixing member 20B for fixing the attachment member 20 to the case 51 is disposed. Thus, if the part which forms the opening part 21 is made to correspond with the part by which the fixing member 20B is arrange | positioned, the arrangement | positioning of the opening part 21 can be performed efficiently and space saving can be achieved. That is, the portion where the fixing member 20 </ b> B for fixing the mounting member 20 to the case 51 is originally required to be formed in a recessed shape. If an opening is formed in the recessed portion to form the opening 21, in addition to the process of recessing a part of the attachment member 20 in order to dispose the fixing member 20 </ b> B, the process of recessing for the attachment member 20. Will not be given specially. Thereby, arrangement | positioning of the opening part 21 can be performed efficiently.

  In the transmission 50, the case 51 may be formed with an inclined portion 51A for guiding the lubricating oil to the opening 21. Thus, when the inclined portion 51A is formed in the case 51 and the lubricating oil is guided to the opening 21 through the inclined portion 51A, the inclined portion 51A is supplied or scattered around the mounting member 20 in the transmission 50. Lubricating oil can be effectively supplied to the opening 21 through the inclined portion 51A. Therefore, the lubricating oil can be reliably supplied to the shift fork 90.

  In the transmission 50, the case 51 is provided with an oil pump 55 that feeds lubricating oil to the transmission 50 and a lubricating oil pipe 56 that guides the lubricating oil from the oil pump 55 to the planetary gear mechanism 10. A discharge port 56H may be formed in the lubricating oil pipe 56 above the inclined portion 51A. Thus, when the discharge port 56H is provided in the lubricant pipe 56 through which the lubricant passes, the lubricant is dripped from the discharge port 56H. Since the discharge port 56H is formed above the inclined portion 51A, the lubricating oil dropped from the discharge port 56H is guided to the opening 21 through the inclined portion 51A. Thereby, the lubricating oil dropped from the lubricating oil pipe 56 can be effectively used for the lubrication of the planetary gear mechanism 10.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Deformation is possible.

DESCRIPTION OF SYMBOLS 10 ... Planetary gear mechanism 11 ... Sun gear 12 ... Pinion gear 13 ... Carrier 15 ... Ring gear 15S ... Stopping member 20 ... Mounting member 20B ... Fixing member 20 ... Stopping member 21 ... Opening part 22 ... Inclined surface 23 ... Fixed side surface 24 ... Outer periphery 40 ... Electric motor 41 ... Rotor 42 ... Stator 50 ... Transmission 51 ... Case 51A ... Inclined portion 51G ... Lubricating oil guide portion 51H ... Lubricating oil outlet 52 ... Pipe insertion portion 55 ... Oil pump 56 ... Lubricating oil pipe 56H ... Discharge port 61 ... No. One input shaft 80 ... 1-speed synchromesh mechanism 90 ... Shift fork

Claims (6)

A sun gear disposed on the rotation shaft, a plurality of pinion gears meshed with the outer diameter side of the sun gear, a carrier supporting the plurality of pinion gears, and a ring gear meshed with the pinion gear on the outer diameter side of the carrier, A planetary gear mechanism comprising;
A connection / disconnection mechanism for connecting / disconnecting the planetary gear mechanism;
An operating member for operating the connection / disconnection mechanism;
A case of a transmission housing the planetary gear mechanism, the connection / disconnection mechanism, and the operation member;
An attachment member for attaching the ring gear of the planetary gear mechanism to the case;
In the mounting member, an opening for introducing lubricating oil is formed above the operation member. An electric motor is disposed on the outer periphery of the ring gear,
The transmission according to claim 1, wherein the opening is disposed at an end portion in an axial direction of the electric motor and below the electric motor. The transmission according to claim 1, wherein the opening has an inclined surface formed so that the opening area increases as it goes upward. The part in which the said opening part is formed is a part by which the fixing member for fixing the said attachment member to the said case is arrange | positioned, The Claim 1 thru | or 3 characterized by the above-mentioned. transmission. The transmission according to any one of claims 1 to 4, wherein the case is formed with an inclined portion for guiding the lubricating oil to the opening. The case is provided with an oil pump that feeds lubricating oil to the transmission, and a lubricating oil pipe that guides the lubricating oil from the oil pump to the planetary gear mechanism,
The transmission according to claim 5, wherein a discharge port is formed in the lubricating oil pipe above the inclined portion.

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