JP2015218865A - Electric drive device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an electric drive device capable of efficiently scooping up lubricant to a high place by a speed reduction mechanism.SOLUTION: An electric drive device scoops up lubricant of a lubricant storage part 15a in a speed reducer chamber 15 with rotation of a speed reduction mechanism 4 for reducing rotational frequency of an electric motor 3 and transmitting it to a unit output shaft 2. In the electric drive device, in a unit case 1, provided are lubricant guide parts 110, 120 that are provided along the outer peripheral part of a driven gear 42 through an interval where lubricant can rise between the unit case 1 and the driven gear 42 of the speed reduction mechanism 4, and extend up to a high place with respect to the oil level of the lubricant storage part 15a.

Description

  The present invention relates to an electric drive device including an electric motor and a speed reduction mechanism.

2. Description of the Related Art Conventionally, in an electric drive device including an electric motor and a speed reduction mechanism, there is known an apparatus in which lubricating oil is scraped up and scattered by a speed reduction mechanism to perform cooling and lubrication (for example, see Patent Document 1). .
In this prior art, the lubricating oil scraped up by the driven gear of the parallel shaft gear train that decelerates in the electric drive device is guided to the rotor shaft, and the amount of lubricating oil flowing in the rotor shaft is ensured to cool the rotor. I am doing so.

JP 2006-248417 A

In the conventional technology as described above, when a cooling object such as an electric motor or a bearing or an object to be lubricated is arranged at the upper part of the electric drive device, it is necessary to scoop up and scatter the lubricating oil up to the height of the device. In particular, increasing the speed reduction ratio of the speed reduction mechanism leads to an increase in the size of the speed reduction mechanism, and the demand for scraping the lubricating oil to a high place increases.
However, in the above-described prior art, the driven gear has the following problem in efficiently scavenging the lubricating oil to a high place.
That is, when the lubricating oil is scraped up, the lubricating oil is scattered in all directions, so it is necessary to secure a sufficient amount of the lubricating oil to be scraped up to a high place. Arise. Thus, in order to secure the total amount of scraping, it is necessary to secure a sufficient amount of lubricating oil stored in the electric drive device, resulting in an increase in the size of the device.
For this reason, it is difficult to ensure the amount of oil to be scraped up to a high place while downsizing the apparatus. In addition, when the total amount of the lubricating oil is increased, the energy consumption for the increase is also increased.
Therefore, as described above, it is difficult for the gear of the speed reduction mechanism to efficiently scrape the lubricating oil to a high place.

  The present invention has been made paying attention to the above problem, and an object of the present invention is to provide an electric drive device capable of efficiently scooping up lubricating oil to a high place by a reduction mechanism.

In order to achieve the above object, the present invention provides:
An electric drive device configured to scrape the lubricating oil in the lubricating oil reservoir in the case by the rotation of a speed reduction mechanism that decelerates the rotation of the electric motor and transmits it to the output shaft,
The case is provided along the outer periphery of the driven gear through a gap capable of raising the lubricating oil between the driven gear of the speed reduction mechanism and extends to a higher position than the oil level of the lubricating oil reservoir. The existing lubricating oil guide part is provided.

In the electric drive device of the present invention, during the rotation of the driven gear, the lubricating oil rises along the lubricating oil guide member without being scattered in the outer diameter direction at the place where the lubricating oil guide member is provided, and then lubricates. The oil guide member scatters in the outer diameter direction of the driven gear beyond the upper end of the oil guide member.
Therefore, compared with the case where the lubricating oil guide member is not provided, the lubricating oil can be efficiently scraped and scattered to a high place.

It is sectional drawing which shows the mounting state to the vehicle of the drive unit to which the electric drive device of Embodiment 1 is applied. It is a figure which shows the reduction gear case applied to the drive unit of FIG. 1, Comprising: (a) is a longitudinal cross-sectional view of a reduction gear case, (b) looked at the reduction gear case from the arrow Y2 direction of Fig.2 (a). It is a front view. It is a figure which shows the motor case applied to the drive unit of FIG. 1, Comprising: (a) is a longitudinal cross-sectional view of a motor case, (b) is the front view which looked at the motor case from the arrow Y3 direction of Fig.3 (a). is there. It is a perspective view which shows the principal part of the said drive unit, Comprising: The state which looked down at the principal part of the drive unit from the arrow Y4 direction of FIG.2 (b) is shown. It is sectional drawing which shows the cross section of the lubricating oil guide part in the said drive unit, Comprising: The cross section in the position of the S5-S5 line | wire of FIG.3 (b) is shown. It is sectional drawing which shows the drive unit to which the electric drive device of Embodiment 2 is applied. FIGS. 7A and 7B are diagrams illustrating a reduction gear case applied to the drive unit of FIG. 6, where FIG. 7A is a longitudinal sectional view of the reduction gear case, and FIG. 7B is a view of the reduction gear case from the direction of arrow Y6 in FIG. It is a front view. It is a figure which shows the motor case applied to the drive unit of FIG. 6, Comprising: (a) is a longitudinal cross-sectional view of a motor case, (b) is the front view which looked at the motor case from the arrow Y7 direction of Fig.8 (a). is there. It is a figure which shows the reduction gear case used for the drive unit to which the electric drive device of Embodiment 3 is applied, Comprising: (a) is a longitudinal cross-sectional view of a reduction gear case, (b) shows a reduction gear case in FIG. It is the front view seen from the arrow Y8 direction. It is a figure which shows the motor case used for the drive unit to which the electric drive device of Embodiment 3 is applied, Comprising: (a) is a longitudinal cross-sectional view of a motor case, (b) is an arrow of Fig.10 (a). It is the front view seen from the Y9 direction. It is sectional drawing which shows the drive unit to which the electric drive device of Embodiment 3 is applied, Comprising: (a) shows the cross section of the position of the Sa-Sa line of FIG.10 (b), (b) is FIG.10 (b). The cross section of the position of the Sb-Sb line | wire of () is shown. It is sectional drawing which shows the drive unit to which the electric drive device of Embodiment 4 is applied, Comprising: (a) shows the cross section of the position similar to Fig.11 (a), (b) is the same as FIG.11 (b). The cross section of the position of is shown.

Hereinafter, the best mode for realizing the electric drive device of the present invention will be described based on the embodiments shown in the drawings.
(Embodiment 1)
The electric drive apparatus according to the first embodiment is applied to a drive unit A that drives drive wheels in a vehicle. First, the overall configuration of the drive unit A will be described.
FIG. 1 is a cross-sectional view showing a drive unit A provided with the rotor shaft cooling structure of the first embodiment. Hereinafter, based on FIG. 1, the whole structure of the drive unit A is demonstrated.

[Mounting status of drive unit A]
First, the mounting state of the drive unit A on the vehicle will be briefly described.
This drive unit A is a so-called in-wheel type drive unit connected to a suspension device of the vehicle in order to drive the front wheel FW of the vehicle as a drive wheel.
As shown in FIG. 1, in the drive unit A, a unit output shaft 2 projects from the unit case 1 in the vehicle exterior direction (arrow OUT direction). In each figure, the arrow UP indicates the vehicle upper direction, the arrow OUT indicates the vehicle outer direction in the vehicle width direction, and the arrow IN indicates the vehicle inner direction in the vehicle width direction.

A wheel hub shaft 103 is serrated to the tip of the unit output shaft 2, and this wheel hub shaft 103 is supported by a knuckle arm 104, which is a component of the suspension device and the steering device, via a hub bearing 105. Yes. A tire wheel 102 that supports the inner periphery of the front wheel FW is bolted to the wheel hub shaft 103 so as to be integrally rotatable.
The knuckle arm 104 is supported by a vehicle body (not shown) so that it can be steered in the horizontal direction around a kingpin shaft passing through an upper pivot and a lower pivot (not shown).

[Configuration of drive unit]
Next, the configuration of the drive unit A will be described.
In the drive unit A, the electric motor 3 and the speed reduction mechanism 4 are accommodated in the unit case 1, and the rotation of the electric motor 3 as a rotating electrical machine is decelerated by the speed reduction mechanism 4 and transmitted to the unit output shaft 2. It has a configuration.

(Unit case structure)
First, the structure of the unit case 1 will be described.
The unit case 1 includes a motor case 11 that covers the outer diameter direction of the electric motor 3, a speed reducer case 12 that covers the outer diameter direction of the speed reduction mechanism 4, and a motor cover 13 that covers the side of the electric motor 3 in the vehicle interior direction. Three parts are connected by bolts. A side cover 13 a that covers the resolver 37 is provided at the axial center of the motor cover 13.

The unit case 1 includes a motor chamber 14 that houses the electric motor 3 and a reduction gear chamber 15 that houses the speed reduction mechanism 4. The speed reducer chamber 15 is a wet space that contains lubricating oil that lubricates gears and bearings described later and also functions as a refrigerant. An oil seal 16 seals between the speed reducer chamber 15 as the wet space and the motor chamber 14 as the dry space.
Further, the electric motor 3 and the motor chamber 14 are arranged at a position above the vehicle with respect to the speed reduction mechanism 4 and the speed reducer chamber 15. The motor case 11 is provided with a partition wall 11 a that partitions the motor chamber 14 and the reduction gear chamber 15. A plurality of heat radiation fins 11 b are raised on the outer periphery of the motor case 11 in the outer diameter direction. Yes.

In addition, the lower part of the reduction gear chamber 15 serves as a lubricating oil reservoir 15a that stores lubricating oil dropped due to gravity.
In FIG. 1, an alternate long and two short dashes line OIL indicates the oil level of the lubricating oil reservoir 15a. When the drive unit A is in operation, the oil level is lowered by lubricating oil that will be described later. Accordingly, in FIGS. 2B and 3B, the two-dot chain line OIL1 indicates the oil level when stationary, and the two-dot chain line OIL2 indicates the oil level when operating. In other figures, when the two-dot chain lines OIL1 and OIL2 are also shown, the former indicates the oil level when stationary, and the latter indicates the oil level during operation.

(Configuration of electric motor)
Next, the configuration of the electric motor 3 will be described.
The electric motor 3 includes a rotor shaft 31, a rotor 32, a stator 33, and a stator coil 34.
The end of the rotor shaft 31 in the vehicle interior direction is rotatably supported by the motor cover 13 by the first bearing 35 while the end of the rotor shaft 31 in the axial direction is rotatable relative to the motor case 11 by the second bearing 36. It is supported by. The first bearing 35 is supported at the inner peripheral position of the motor cover 13 in the axial direction. On the other hand, the second bearing 36 is supported on the outer periphery of a bearing support member 70 fixed to the partition wall 11a. Note that the rotor shaft center line of the rotor shaft 31 is offset from the tire shaft center line of the unit output shaft 2 above the vehicle (arrow UP in FIG. 1).

The rotor 32 is fixed to the outer periphery of the rotor shaft 31 and is composed of a laminated steel plate in which a permanent magnet is embedded.
The stator 33 is composed of laminated stator teeth around which a stator coil 34 is wound. The stator 33 is disposed on the outer peripheral side of the rotor 32 with a radial air gap between the rotor 32 and fixed to the motor case 11.

  The electric motor 3 can rotate the rotor shaft 31 by applying a three-phase alternating current to the stator coil 34 (powering), while the rotor shaft 31 rotates the three-phase alternating current to the stator coil 34. It can be generated (regeneration). A resolver 37 for detecting the motor rotation angle is provided at the end position of the rotor shaft 31 on the vehicle interior side.

(Configuration of deceleration mechanism)
Next, the speed reduction mechanism 4 will be described.
The speed reduction mechanism 4 includes a parallel shaft gear train 40 disposed on the vehicle inner side in the axial direction, and a planetary gear mechanism 50 disposed on the vehicle outer side in the axial direction.
The parallel shaft gear train 40 decelerates the rotation of the rotor shaft 31 of the electric motor 3 to the unit output shaft 2 in the first stage and transmits it to the planetary gear mechanism 50. The planetary gear mechanism 50 is in the second stage. Is transmitted to the unit output shaft 2. Therefore, the parallel shaft gear train 40 rotates at a relatively high speed, and the planetary gear mechanism 50 rotates at a relatively low speed. In addition, by performing two-stage deceleration in this way, it is possible to use a high-speed small motor as the electric motor 3.

The parallel shaft gear train 40 includes a drive gear 41 formed at the end of the rotor shaft 31 in the vehicle exterior direction, a driven gear 42 that meshes with the drive gear 41 and has a larger diameter than the drive gear 41, and the driven gear 42. And a driven shaft 43 provided in parallel with the rotor shaft 31.
The driven gear 42 is arranged so as to be partly immersed in the lubricating oil in the lubricating oil reservoir 15a formed in the unit case 1 below the tire axis center line. The amount of lubricating oil and the position of the driven gear 42 are set so that the driven gear 42 is immersed in the lubricating oil even when the oil level of the lubricating oil is reduced to the oil level (OIL2) during operation. Yes.

The driven shaft 43 is supported such that the motor side shaft end portion is rotatable with respect to the motor case 11 via the third bearing 45, and the wheel side shaft end portion is rotatable with respect to the unit output shaft 2 via the fourth bearing 46. It is supported by.
Further, the rotation center axis Cout of the driven shaft 43 and the unit output shaft 2 is in the vehicle longitudinal direction (arrow FR) with respect to the rotation center axis Cmot of the electric motor 3, as shown in FIGS. 2 (b) and 3 (b). Direction).
That is, the cylindrical portion 11c is erected on the partition wall 11a of the motor case 11 in the axial direction toward the outside of the vehicle. And the 3rd bearing 45 is interposed between the inner periphery of this cylindrical part 11c, and the outer periphery of the edge part of the driven shaft 43 in the vehicle interior direction.
The distal end of the driven shaft 43 at the end in the vehicle outer direction is inserted into the inner periphery of the unit output shaft 2, and the fourth bearing 46 is interposed between the outer periphery of the driven shaft 43 and the inner periphery of the unit output shaft 2. ing. The support structure for the unit output shaft 2 will be described later.

  Further, the driven shaft 43 is formed with a through-shaft oil passage 47 at the axial position. Although details of the through-shaft oil passage 47 are omitted, the lubricating oil is supplied from a structure that is provided in the partition wall 11a and catches and supplies the lubricating oil scraped up in the speed reducer chamber 15. The bearing 46 and a fifth bearing 48 described later are lubricated.

Next, the configuration of the planetary gear mechanism 50 will be described.
The planetary gear mechanism 50 is provided adjacent to the vehicle outer direction side in the axial direction of the parallel shaft gear train 40. The planetary gear mechanism 50 includes a sun gear 51 integrated with the driven shaft 43, a plurality of pinion gears 52 that mesh with the sun gear 51, a pinion carrier 53 that supports the pinion gear 52, and a ring gear that meshes with the pinion gear 52 and is fixed to the speed reducer case 12. 54. That is, the planetary gear mechanism 50 is a reduction gear mechanism that decelerates the input rotation from the sun gear 51 and outputs it to the pinion carrier 53 by fixing the ring gear 54 to the case.

In the first embodiment, the ring gear 54 and the driven gear 42 are formed to have substantially the same diameter. As shown in FIG. 1, the ring gear 54 and the driven gear 42 are arranged in the axial direction of the outer peripheral portion where the gear of the driven gear 42 is formed. The side surface of the ring gear 54 is disposed adjacently.
The rotation center axis of the planetary gear mechanism 50 is arranged coaxially with the rotation center axis (tire axis center line) between the driven gear 42 and the unit output shaft 2.

The ring gear 54 is fixed to the speed reducer case 12 as follows.
That is, the reduction gear case 12 is provided with a cylindrical internal gear supporting cylindrical portion 12b erected in the axial direction as shown in FIG. A plurality of groove-like engagement grooves 12c that are concave in the outer diameter direction and extend in the axial direction are formed on the inner periphery of the cylindrical portion 12b for supporting the internal gear.

  On the other hand, on the outer periphery of the ring gear 54 shown in FIG. 1, although not shown in the drawing, a protruding strip that protrudes in the outer diameter direction and extends in the axial direction is formed in the engagement groove 12 c so as to be insertable in the axial direction. ing. Therefore, the circumferential movement of the ring gear 54 is restricted by engaging the protrusions of the ring gear 54 and the engagement grooves 12c of the speed reducer case 12 in the circumferential direction. These engagement grooves 12c and the ridges engaged therewith constitute a fixing portion for fixing the ring gear 54 to the speed reducer case 12. The movement of the ring gear 54 in the axial direction is achieved by abutment of the engagement groove 12c on the end surface in the axial direction and engagement in the axial direction by the washer 54w.

  In the first embodiment, as shown in FIG. 2 (b), the engagement groove 12c is provided at the upper part and the lower part of the internal gear supporting cylindrical part 12b, and is not provided at the intermediate part thereof. . This is because the reduction gear side guide portions 111 and 121 described later are formed in the intermediate portion. Details of the reduction gear side guide portions 111 and 121 will be described later.

(Lubricating structure for lubricating oil)
When the electric motor 3 is driven, the lubricating oil stored in the lubricating oil storage portion 15a shown in FIG. 1 is scraped up by the driven gear 42, and the bearings 36, 45, 46, and 48 in the reduction gear chamber 15 are decelerated. The mechanism 4 is lubricated and the rotor shaft 31 is cooled.

  In the first embodiment, when the driven gear 42 scoops up the lubricating oil, in the reduction gear chamber 15, the lubricating oil guide unit 110, so that the lubricating oil is efficiently scooped up and scattered up to a high place. 120 is provided.

  These lubricating oil guide portions 110 and 120 are disposed with a slight gap with respect to the outer diameter side and the side surface of the outer peripheral portion of the driven gear 42 and are above the lubricating oil surface. Thus, the driven gear 42 extends upward from the rotation center axis Cout.

  The lubricating oil guide portions 110 and 120 described above are formed in the pair of reduction gear side guide portions 111 and 121 formed in the reduction gear case 12 shown in FIG. 2B and the motor case 11 shown in FIG. The pair of motor side guide portions 112 and 122 thus formed are abutted against each other in the axial direction.

FIGS. 4 and 5 show the abutting state of the reduction gear side guide portions 111 and 121 and the motor side guide portions 112 and 122 in the axial direction.
FIG. 4 is a perspective view showing a state in which the reduction gear side guide portion 121 (111) and the motor side guide portion 122 (112) are abutted in the axial direction (arrow IN-OUT direction). The state which looked down from the arrow Y4 direction of FIG.2 (b) is shown.
FIG. 5 is a cross-sectional view showing a cross section of the drive unit A at the position of the line S5-S5 in FIG.

The reduction gear side guide portions 111 and 121 are arranged in an arc along the driven gear 42 at a position where a gap is formed in the outer diameter direction of the outer peripheral portion of the driven gear 42. The reduction gear side guide portions 111 and 121 are formed by an intermediate portion in the vertical direction that does not have the engaging groove 12c as a fixing portion in the above-described internal gear supporting cylindrical portion 12b. The side surfaces 54s of the ring gear 54 fixed to the internal gear supporting cylindrical portion 12b are side surfaces of the reduction gear side guide portions 111 and 121 provided at intervals along the side surface of the outer peripheral portion of the driven gear 42. It constitutes a guide part.
On the other hand, the motor side guide portions 112 and 122 are provided by surrounding the corner portions of the outer periphery of the driven gear 42 in an L shape by the outer periphery guide portions 112a and 122a and the side surface guide portions 112b and 122b. The outer periphery guide parts 112a and 122a are arranged along the outer periphery with a gap between the outer periphery of the driven gear 42 and the outer periphery. Further, the side guide portions 112 b and 122 b are disposed along the side surface of the driven gear 42.

  Therefore, the outer peripheral portion of the driven gear 42 is spaced in the outer diameter direction by the reducer-side guide portions 111 and 121 of the lubricant guide portions 110 and 120 and the outer peripheral guide portions 111a and 121a of the motor-side guide portions 112 and 122. Covered. Further, the side surface of the outer peripheral portion of the driven gear 42 is covered with a space by the side surface guide portions 112 b and 122 b of the motor side guide portions 112 and 122 and the side surface 54 s of the ring gear 54.

And the space | interval provided between the outer periphery of the driven gear 42 and the lubricating oil guide parts 110 and 120 is a space | interval which can raise lubricating oil at the time of the driven gear 42 rotation.
Therefore, when the driven gear 42 rotates, the lubricating oil is lifted upward along the outer peripheral portion of the driven gear 42 and the lubricating oil guide portions 110 and 120. Further, after reaching the upper ends of both the lubricating oil guide portions 110 and 120, they are scattered in the outer diameter direction as indicated by arrows OIa and OIb in FIGS. 2 (b) and 3 (b). The arrow OIa indicates the lubricating oil scattered from between the driven gear 42 and the upper end of the lubricating oil guide 120, and the arrow OIb indicates that the scattered lubricating oil further collides with the speed reducer case 12 and is scattered. It shows a change of direction.

(Catch structure)
Next, a description will be given of a catch structure that receives the scraped lubricating oil when it is dropped and supplies it to a through-shaft oil passage 47 formed in the driven shaft 43.
This catch structure includes lower catch portions 130 and 140 shown in FIG. 3B, communication passages 151 and 152, and a lubricating oil supply port 160.

The lower catch portions 130 and 140 receive the lubricating oil that falls after being scattered in the speed reducer chamber 15, and in the horizontal direction (left and right direction in FIG. 3B), both sides (in the drawing) of the rotation center axis Cout of the driven gear. It is provided on both the left and right sides.
That is, the lower catch portions 130 and 140 can receive the lubricating oil even when the direction of the lubricating oil scraping of the driven gear 42 is reversed between when the vehicle moves forward and when the vehicle moves backward. In general, since the vehicle has a higher forward frequency than reverse, it is desirable that the lower catch portions 130 and 140 be provided at least on the side where the amount of falling lubricant oil is large when the vehicle moves forward.

In the first embodiment, the lower catch portions 130 and 140 are provided across the motor case 11 and the speed reducer case 12 in the same manner as the lubricant guide portions 110 and 120.
The lower catch portions 130 and 140 are formed by abutting the reduction gear side catch portions 131 and 141 shown in FIG. 2B and the motor side catch portions 132 and 142 shown in FIG. 3B in the axial direction. Yes.

As shown in FIG. 2B, the reduction gear side catch portions 131 and 141 are arranged in such a manner that the outer diameter side of the reduction gear side guide portions 111 and 121 of the internal gear supporting cylindrical portion 12b and the reduction gear case 12 are horizontally aligned. Are connected to each other by plate-like bottom plate portions 131a and 141a which are formed in a concave shape.
As shown in FIG. 3B, the motor-side catch portions 132 and 142 are formed in a concave shape when viewed from the axial direction. That is, the motor-side catch portions 132 and 142 are formed in a plate shape extending in the horizontal direction between the outer diameter side of the outer peripheral guide portions 112a and 122a of the motor-side guide portions 112 and 122 and the inner periphery of the motor case 11. The bottom plate portions 132a and 142a are connected to each other.

Since the lower catch portions 130 and 140 formed as described above are formed in a concave shape opened upward, the lubricant oil falling from above can be received in the reducer chamber 15.
Further, the lubricating oil received by the lower catch portions 130 and 140 is supplied to the lubricating oil supply port 160 via the both communication paths 151 and 152.
First, the lubricating oil supply port 160 will be described.

  As shown in FIG. 1, the lubricating oil supply port 160 is formed by an inner portion of a cylindrical portion 11 c that supports the driven shaft 43 in the motor case 11, and is arranged coaxially with the driven shaft 43. The lubricating oil supply port 160 is communicated with the through-shaft oil passage 47 of the driven shaft 43. Further, in the first embodiment, the lubricating oil of the lubricating oil supply port 160 is guided to the through-shaft oil passage 47. A funnel-shaped guide 161 is provided. That is, the guide 161 is provided with a tube-like introduction pipe inserted into the through-shaft oil passage 47, and the lubricating oil supplied to the lubricating oil supply port 160 from the communication passages 151 and 152 described later is efficiently passed through the through-shaft center. Guide to oil passage 47.

As described above, the lubricating oil supply port 160 is connected to the lower catch portions 130 and 140 via the communication paths 151 and 152.
That is, as shown in FIG. 1, a communication recess 160 a is formed in the lower portion of the lubricating oil supply port 160 in the axial direction and in the direction approaching the electric motor 3. As shown in FIG. 3B, the motor case 11 has a hole that forms the communication passages 151 and 152 at a position overlapping the communication recess 160a in the axial direction. The tip is opened in the communication recess 160a.

  Furthermore, notch parts 132b and 142b which connect each lower catch part 130 and 140 and the communicating paths 151 and 152 in the corner part of the motor side catch parts 132 and 142 are formed. Thereby, each lower catch part 130 and 140 is connected to the lubricating oil supply port 160, respectively.

Moreover, in this Embodiment 1, the structure which catches the lubricating oil for cooling the rotor shaft 31 is also provided in the upper part of the reduction gear chamber 15, The structure is demonstrated easily.
That is, the motor case 11 has upper catch portions 113 and 114 formed in an L-shaped cross-section so as to receive the lubricating oil that has been scraped up and scattered in the upper portion of the reduction gear chamber 15. It is provided at approximately the same height as the position. The lubricating oil received by these upper catch portions 113 and 114 is configured to be supplied to the rotor shaft 31 through a flow path provided in the bearing support member 70, although the details thereof are omitted. ing.
Further, an air breather chamber 170 for communicating the outside with the reduction gear chamber 15 is provided further above the upper catch portions 113 and 114, and for preventing the lubricating oil from entering the air breather chamber 170. A plate-like cover plate 171 is provided. The cover plate 171 is inclined downward in the direction of the upper catch portions 113 and 114 so that the lubricating oil that collides and adheres to the lower surface of the cover plate 171 falls to the upper catch portions 113 and 114.

(Operation of Embodiment 1)
Below, the effect | action of the electric drive device of Embodiment 1 is demonstrated.
When the electric motor 3 is driven, when the electric motor 3 is driven, the rotor shaft 31 rotates, and this rotation is decelerated by the parallel shaft gear train 40 and transmitted to the driven shaft 43. The rotation of the driven shaft 43 is further decelerated by the planetary gear mechanism 50 and transmitted to the unit output shaft 2, and the front wheel FW is rotated.

  When the electric motor 3 is driven, the lubricating oil stored in the lubricating oil storage portion 15 a is scraped up by the driven gear 42 and the pinion gear 52 and the pinion carrier 53 of the planetary gear mechanism 50. The bearings 45, 46, and 48 and the speed reduction mechanism 4 are lubricated by the scraped lubricating oil.

Further, the lubricating oil scraped up in the reduction gear chamber 15 is received by the catch portions 130, 140, 113, and 114. Then, the lubricating oil received by the lower catch portions 130 and 140 is supplied to the through-shaft oil passage 47 of the driven shaft 43. Due to the supply of the lubricating oil through the through-shaft oil passage 47, the lubricating oil that has been separated from the driven gear 42 in the axial direction and that has been scattered by the planetary gear mechanism 50 interposed between the driven gear 42 and the driven gear 42 is scraped. Lubricating oil is stably supplied to both bearings 46 and 48 which are difficult to reach.
Note that the lubricating oil received by the upper catch portions 113 and 114 is supplied to the rotor shaft 31 and is cooled, but the details thereof are omitted.

Next, a description will be given of scooping up the lubricating oil by the driven gear 42.
In the first embodiment, when the lubricating oil is scraped up by the rotation of the driven gear 42, the lubricating oil rises between the driven gear 42 and one of the lubricating oil guide portions 110 and 120. The upper part of the lubricant guide portions 110 and 120 scatters upward.
FIG. 2B and FIG. 3B respectively show an example of a scattering state due to the scraping of the lubricating oil during forward traveling of the vehicle by arrows OIa and OIb.

  In the illustrated example, the driven gear 42 rotates counterclockwise in FIG. 2B and rotates clockwise in FIG. 3B. In this case, within the range in which the lubricating oil guide part 120 is provided in the vertical direction, the lubricating oil guide part 120 prevents the lubricating oil from scattering in the outer diameter direction due to centrifugal force when the driven gear 42 rotates. . The interval between the driven gear 42 and the lubricating oil guide portion 120 is set to a gap where the lubricating oil does not fall. Therefore, when the driven gear 42 rotates, the lubricating oil moves along the lubricating oil guide portion 120. To rise. In this case, the lubricating oil guide portion 120 is covered not only in the outer diameter direction of the driven gear 42 but also in the lateral direction (axial direction) by the side guide portion 122b and the side surface 54s of the ring gear 54. It rises without scattering in the axial direction.

  Then, the raised lubricating oil is scattered in the outer diameter direction of the driven gear 42 by centrifugal force from the time when the upper end of the lubricating oil guide portion 120 is exceeded. Therefore, as shown by the arrow OIa, the lubricating oil scatters upward and counterclockwise in FIG. 2B and upward and clockwise in FIG. 3B.

Therefore, the lubricant starts to scatter from a higher position than when the lubricant guide portion 120 is not provided, and the dispersion degree of the scatter is reduced by the lubricant guide portion 120, so that the lubricant guide portion 120 of the driven gear 42 is reduced. It scatters intensively in the direction of rotation. Thereby, in each catch part 113,114,130,140 divided into right and left in FIG.3 (b), lubricating oil is mainly received by both catch part 113,130.
When the vehicle moves backward, the driven gear 42 rotates in the opposite direction to the above, and the lubricating oil scatters in the opposite direction and is mainly received by the upper catch portion 114 and the lower catch portion 140.

  The lubricating oil received by the lower catch portions 130 and 140 is sucked by the negative pressure generated in the through-shaft oil passage 47. That is, due to the centrifugal force generated with the rotation of the driven shaft 43 and the planetary gear mechanism 50, the lubricating oil in the through-shaft center oil passage 47 is, as shown by the arrow OIh in FIG. Spatter in the outer diameter direction. As a result, the lubricating oil is sent to the parts such as the bearings 46 and 48 and the planetary gear mechanism 50 that require lubrication. In addition, the lubricating oil is scattered by the centrifugal force, so that a negative pressure is generated in the through-shaft oil passage 47.

As described above, the amount of lubricating oil that is received by the upper catch portions 113 and 114 disposed at a high position as shown by the arrow OIb in FIG. Will increase. Thereby, the cooling performance in the rotor shaft 31 is improved.
Further, the amount of lubricating oil received by the lower catch portions 130 and 140 increases due to the concentrated scattering of the lubricating oil in the rotational direction of the driven gear 42. As a result, the amount of lubricating oil supplied from the lubricating oil supply port 160 to the through-shaft oil passage 47 is increased, and the lubricating performance of the bearings 46 and 48 separated from the driven gear 42 in the axial direction can be secured more stably. .

  In addition, since the lubricating oil is efficiently received by the lower catch portions 130 and 140 and the upper catch portions 113 and 114 as described above, the amount of lubricating oil agitation that is the amount of lubricating oil floating in the reducer chamber 15 is greatly increased. Can be reduced. For this reason, intrusion of lubricating oil into the air breather chamber 170 can be avoided, and adverse effects on the air breather function can be suppressed.

(Effect of Embodiment 1)
The effects of the electric drive device according to Embodiment 1 are listed below.
1) The electric drive device of Embodiment 1 is
The unit case 1 accommodates an electric motor 3 and a speed reduction mechanism 4 that decelerates the rotation of the electric motor 3 and transmits it to the unit output shaft 2, and lubricates the unit case 1 by the rotation of the speed reduction mechanism 4. An electric drive unit configured to scoop up the lubricating oil in the oil reservoir 15a,
The speed reduction mechanism 4 includes a drive gear 41 that is rotated by the electric motor 3 and a driven gear 42 that rotates while meshing with the drive gear 41 to scoop up the lubricating oil. With
The unit case 1 is provided along the outer periphery of the driven gear 42 through a gap capable of raising the lubricating oil between the driven gear 42 and the oil level of the lubricating oil reservoir 15a. Lubricating oil guide portions 110 and 120 extending to a place are provided.
Therefore, when the driven gear 42 rotates, the lubricating oil moves in the outer diameter direction of the driven gear 42 by centrifugal force in a range where the lubricating oil guide portions 110 and 120 are provided at a position above the oil level of the lubricating oil reservoir 15a. It is prevented from scattering. And according to the rotation direction of the driven gear 42, the lubricating oil rises along either the driven gear 42 or both the lubricating oil guide portions 110, 120, and either one of the lubricating oil guide portions 110, 120 is raised. After exceeding the upper end, it is scattered in the outer diameter direction by centrifugal force.
Therefore, it is possible to scatter the lubricating oil up to a high place without increasing the amount of lubricating oil, and efficiently scrape the lubricating oil up to a high place as compared with the case where the lubricating oil guide portions 110 and 120 are not provided. Is possible.

2) The electric drive device of Embodiment 1 is
The speed reduction mechanism 4 includes a planetary gear mechanism 50 that inputs rotation of the driven gear 42 and transmits the rotation to the unit output shaft 2 at a reduced speed.
The reduction gear case 12 of the unit case 1 is provided with an internal gear support cylindrical portion 12b that forms a cylindrical shape along the outer periphery of the ring gear 54 of the planetary gear mechanism 50 and supports the ring gear 54,
The engagement between the inner gear supporting cylindrical portion 12b and the ring gear 54 as a fixing portion for fixing the ring gear 54 to the inner gear supporting cylindrical portion 12b at a position excluding the intermediate portion in the vertical direction. Providing a groove 12c and ridges,
The lubricating oil guide portions 110 and 120 are formed by reduction gear side guide portions 111 and 121 provided in an intermediate portion of the internal gear supporting cylindrical portion 12b that does not have the engagement groove 12c.
In forming the lubricating oil guide portions 110 and 120, since the internal gear supporting cylindrical portion 12b necessary for supporting the ring gear 54 is used, the lubricating oil guide portions 110 and 120 are formed independently. Thus, the manufacturing is easy and the cost can be reduced.

3) The electric drive device of Embodiment 1 is
In the speed reducer chamber 15 that houses the speed reduction mechanism 4 of the unit case 1, lower catch portions 130 and 140 that receive the lubricating oil scraped up by the driven gear 42 are provided.
The lubricant guide portions 110 and 120 and the lower catch portions 130 and 140 are provided on at least one of both sides of the rotation center axis Cout in the horizontal direction perpendicular to the rotation center axis Cout of the driven gear 42. And
Therefore, if the rotation direction of the driven gear 42 is a constant direction, the lower catch portion 130 (140) is provided at a position where the lubricating oil can be received when rotating in that direction, so that the lubricating oil can be received efficiently. Become. Further, for example, even if the vehicle rotates in both forward and reverse directions as in a vehicle, the lubricating oil can be reliably received by the lower catch portion 130 (140) during either rotation. In addition, it is preferable to provide the lower catch part 130 (140) in the position which can receive lubricating oil at the time of rotation of a direction with high rotation frequency.

4) The electric drive device of Embodiment 1 is
When the lubricating oil guide portions 110 and 120 and the lower catch portion 130 (140) are placed on both sides of the rotation center axis Cout of the driven gear 42 in the horizontal direction, the lubricating oil drops when the vehicle is traveling forward in a vehicle mounted state. It is provided on the side where the amount is large.
Generally, since the vehicle has a higher forward frequency than the reverse, the lower catch portion 130 (140) can efficiently receive the lubricating oil by providing it on the side where the amount of the lubricating oil falls when traveling forward. become.

5) The electric drive device of Embodiment 1 is
The unit case 1 is provided coaxially with a rotation center axis Cout of a driven shaft 43 that supports the driven gear 42 and rotates integrally with the driven gear 42, and allows the lubricating oil to pass through the center axis of the driven shaft 43. A lubricating oil supply port 160 for supplying the oil passage 47;
The lubricating oil guide portions 110 and 120 and the lower catch portions 130 and 140 are provided on both sides in the horizontal direction across the rotation center axis Cout of the driven gear 42,
The lower catch portions 130 and 140 and the lubricating oil supply port 160 communicate with each other through communication passages 151 and 152, respectively.
Since the lubricating oil guide portions 110 and 120 and the lower catch portions 130 and 140 are provided on both sides in the horizontal direction with the rotation center axis Cout interposed therebetween, the lubricating oil can be used regardless of whether the vehicle is moving forward or backward. It can be efficiently received by the lower catch portions 130 and 140. In addition, the same effect can be obtained even when the drive unit A is shared by the left and right wheels.
In addition, each of the lower catch portions 130 and 140 communicated with the lubricating oil supply port 160 through independent communication passages 151 and 152, respectively. For this reason, it is possible to reduce the size of the drive unit A by reducing the axial dimension of the drive unit A, as compared with the case where the communication path connecting both the lower catch portions 130 and 140 is connected to the lubricating oil supply port 160.
That is, when the lower catch portions 130 and 140 are communicated with each other while avoiding the lubricating oil supply port 160, there is a restriction due to the presence of the electric motor 3 and the third bearing 45, and the axial direction of the unit case 1 (motor case 11). It is difficult to provide a communication path without enlarging the dimensions of the. Therefore, by communicating with the lubricating oil supply port 160 through the independent communication paths 151 and 152, the degree of freedom in design is improved, and it is easy to secure the communication paths 151 and 152 while suppressing the axial dimension.

6) The electric drive device of Embodiment 1 is
Lubricating oil guide portions 110 and 120 include outer peripheral guide portions 111a, 121a, 112a, and 122a provided to cover the outer diameter direction of the driven gear 42, and side guide portions 112b that are provided to cover the side surface of the driven gear 42. 122b and side surface 54s.
Therefore, the lubricating oil rising along the lubricating oil guide portions 110 and 120 is scattered in the lateral direction perpendicular to the outer diameter direction with respect to the outer circumferential guide portions 111a, 121a, 112a, and 122a. It is suppressed by 122b and the side surface 54s. Therefore, it is possible to efficiently scrape the lubricating oil as compared with the case where the side guide portions 112b and 122b and the side surface 54s are not provided.

7) The electric drive device of Embodiment 1 is
The side guide portion is configured by a side surface 54s of a ring gear 54 provided in the axial direction of the driven gear 42.
Therefore, compared with the case where a rib or the like is erected so as to have an L-shaped cross section in the reduction gear side guide portions 111 and 121 of the internal gear supporting cylindrical portion 12b and the side surface of the driven gear 42 is covered. Is easy, and the dimension in the axial direction can be suppressed.

8) The electric drive device of Embodiment 1 is
The unit case 1 is divided into a motor case 11 arranged in the outer diameter direction of the electric motor 3 and a speed reducer case 12 arranged in the outer diameter direction of the speed reduction mechanism 4 in the axial direction.
Motor-side catch portions 132, 142 as first catch portion forming portions formed on the motor case 11 with bottom plate portions 132a, 142a, 131a, 141a as bottom portions of the lower catch portions 130, 140, and the speed reducer The reduction gear side catch portions 131 and 141 as the second catch portion forming portions formed on the case 12 are formed by abutting in the axial direction.
Therefore, it is possible to easily form the lower catch portions 130 and 140 over the entire axial width of the reduction gear chamber 15.

(Other embodiments)
Next, an electric drive device according to another embodiment will be described.
In the description of the other embodiments, the same reference numerals as those in the first embodiment are assigned to the same components as those in the first embodiment, and the description thereof is omitted. Only the differences from the first embodiment will be described. .

(Embodiment 2)
The electric drive device of the second embodiment is different from the first embodiment in the structure of the lower catch portions 230 and 240, the communication passage 250, and the lubricating oil supply port 260 shown in FIGS.
That is, the second embodiment is an example in which the electric motor 203 has a large diameter that interferes with the communication recess 160a shown in the first embodiment, and the axial dimension is not enlarged. .

As shown in FIG. 6, the electric motor 203 is formed to have an outer diameter that overlaps the driven shaft 43 and the rotation center axis Cout of the unit output shaft 2 in the radial direction. Therefore, the lower end portion of the cylindrical portion that supports the stator 33 in the motor case 211 is disposed at substantially the same position in the vertical direction as the lower end portion of the cylindrical portion 211 c that supports the inner periphery of the third bearing 45.
Therefore, when the communication recess 160a that is recessed in the axial direction is provided in the lubricating oil supply port 160 shown in the first embodiment, it is necessary to separate the electric motor 203 and the parallel shaft gear train 40 in the axial direction. The axial dimension of the drive unit is enlarged.

Therefore, in the second embodiment, the lubricating oil supply port 260 is provided with a communication hole 260a obliquely in the outer diameter direction from the lubricating oil supply port 260, instead of the communication concave portion 160a that is recessed in the axial direction. .
The communication hole 260a is for communicating with a communication passage 250 that communicates the lower catch portions 230 and 240. In the second embodiment, as shown in FIG. 8 (b), the communication passage 250 moves the lower position of the lubricating oil supply port 260 from one lower catch portion 240 to the other lower catch portion 230. And is formed in a straight line obliquely downward.

That is, in the first embodiment, the communication passages 151 and 152 are arranged at the same height as the lubricating oil supply port 160 at the same position as the communication recess 160a in the axial direction, and both communicate with each other. The motor case 211 needs to have an axial dimension.
Therefore, in the second embodiment, the communication path 250 is disposed at a position lower than the lubricating oil supply port 260, and the axial dimension is shortened compared to the case where both are disposed at the same height. ing.

  Further, in the second embodiment, one lower catch portion 230 of both the lower catch portions 230 and 240 is provided with a lower extension portion 230e that extends downward from the other lower catch portion 240. By providing the lower extension 230 e in this manner, the communication path 250 can be disposed at a position lower than the lubricating oil supply port 260.

  That is, the downward extension 230e is configured so that the motor-side catch 231 and the bottom plate portions 231a and 232a of the speed reducer-side catch 232 that are abutted in the axial direction are shown in FIGS. 7B and 8B, respectively. In addition, it extends downward along the lubricating oil guide 120 with a gap. Accordingly, the lower extension 230e extends to a position lower than the other lower catch 240.

  The other lower catch portion 240 is also formed by abutting the reduction gear side catch portion 241 and the motor side catch portion 242 in the axial direction, as in the first embodiment. The difference from the first embodiment is that the bottom plate portions 241a and 242a are inclined so as to be positioned closer to the inner diameter direction side in accordance with the inclination of the communication path 250 described later.

  As shown in FIG. 8B, the communication path 250 extends downward from one end of the motor case 11 through the tip of the communication hole 260a at a position adjacent to both the lower catch portions 230 and 240 in the axial direction. It is formed in a straight line toward the position adjacent to the portion 230e. The communication passage 250 and the lower catch portions 230 and 240 communicate with the communication passage 250 in the motor case 211 and open to the side surfaces of the lower catch portions 230 and 240 in the same manner as in the first embodiment. 232b and 242b communicate with each other.

Therefore, the lower catch part 230 is connected via the communication hole 260a, the notch part 232b, and the part (the part corresponding to the 1st communication path) which connects the communication hole 260a and the notch part 232b in the communication path 250. The lubricating oil supply port 260 is communicated.
The other lower catch part 240 is connected via the communication hole 260a, the notch part 242b, and a part (a part corresponding to the second communication path) that connects the communication hole 260a and the notch part 242b in the communication path 250. In this manner, the lubricating oil supply port 260 is communicated.

(Operation of Embodiment 2)
Next, the operation of the second embodiment will be described. In describing this action, differences from the first embodiment will be described.
In the second embodiment, the lower catch portions 230 and 240 are always communicated with each other through the communication path 250. For this reason, in both the lower catch portions 230 and 240, the lubricating oil amount of the lower catch portions 230 and 240 of the oil level of the both lower catch portions 230 and 240 is determined even when the lubricating oil is mainly received according to the rotational direction of the driven gear 42. Uniformity is achieved.
Therefore, as compared with the case where both the lower catch portions 230 and 240 are independently communicated with the lubricating oil supply port 260, the lubricating oil can be stably supplied to the through-shaft oil passage 47.

  That is, when the driven shaft 43 rotates at a high speed, the amount of lubricating oil scattered from the through-shaft center oil passage 47 in the outer diameter direction increases, and the amount of lubricating oil received by the lower catch portions 230 and 240 also increases. In this case, the surplus amounts of the lower catch portions 230 and 240 overflow from the lower catch portions 230 and 240 or the lubricating oil supply port 260.

  On the other hand, in the second embodiment, since the lower catch portions 230 and 240 are always communicated with each other via the communication path 250, the oil amount of the lower catch portions 230 and 240 is leveled. Therefore, at the time of high rotation of the driven shaft 43, especially in the initial rotation when the scraping amount is small, the lubricating oil that is stored on the opposite side of the lower side of the lubricating oil of the lower catch portions 230, 240 is It becomes a compensation amount, and stable supply of lubricating oil becomes possible.

  In addition, since the communication path 250 is formed in a straight line, it is possible to process in one process, and compared to the case where both lower catch portions 230 and 240 are independently connected to the lubricating oil supply port 260, Processing costs can be reduced by reducing the number of processing steps.

(Effect of Embodiment 2)
In addition to the effects 1) to 8) described above, the electric drive device of the second embodiment has the effects listed below.
2-1) The electric drive device of Embodiment 2 is
One of the lower catch portions 230, 240 on both sides is provided with a lower extension portion 230e extending below the lubricating oil supply port 260 along the lubricating oil guide portion 110,
A communication path 250 between the lower catch portion 230 on the side where the lower extension portion 230e is formed and the lubricating oil supply port 260 is connected to the lower extension portion 230e.
Therefore, it is possible to form the communication path 250 that communicates the lower extension 230 e and the lubricating oil supply port 260 at a position below the lubricating oil supply port 260. Therefore, the axial dimension of the motor case 11 necessary for forming the communication path 250 can be suppressed as compared with the case where the communication path 250 is arranged at the same height as the lubricating oil supply port 260. .

  In particular, as in the second embodiment, when the outer diameter dimension of the electric motor 203 is arranged so as to overlap the lubricating oil supply port 260 in the vertical direction, the axial interval between the two 203 and 260 is reduced, It is possible to reduce the axial dimension of the drive unit itself.

2-2) The electric drive device of Embodiment 2 is
A first communication path (a part of the communication path 250) connected to the lower extension 230e and a second communication path (the communication path 250 of the communication path 250) connected to the lower catch part 240 not provided with the lower extension 230e. The communication passage 250 is arranged in a straight line.
Therefore, in forming the communication path 250, it can be formed by drilling work from one direction, and the processing cost can be reduced.

Further, in the second embodiment, the lower catch portions 230 and 240 are directly communicated with each other through the communication passage 250, and the communication passage 250 is communicated with the lubricating oil supply port 260 through the communication hole 260a.
Therefore, it is possible to level the oil level of the lower catch portions 230 and 240, and the amount of lubricating oil stored in the lower catch portions 230 and 240 can be secured. This makes it possible to stabilize the lubrication performance.

(Embodiment 3)
As shown in FIGS. 10A and 10B, the electric drive device of the third embodiment communicates both lower catch portions 330 and 340 separately from the communication passage 350 for communication with the lubricating oil supply port 260. In this example, the pipes 351 communicate with each other.

  The lower catch portions 330 and 340 are respectively provided on the reducer side catch portions 331 and 341 formed in the reducer case 312 shown in FIG. 9B and the motor side formed in the motor case 311 shown in FIG. The catch portions 332 and 342 are formed to abut against each other in the axial direction. This is the same as in the first and second embodiments.

  9 (b) and 10 (b), the bottom plate portions 331a, 341a, 332a, and 342a of the lower catch portions 330 and 340 are used to hold pipes that are semicircular when viewed from above. Notches 331b, 341b, 332b, and 342b are formed. These pipe clamping notches 331b, 341b, 332b, and 342b are inserted into the inner diameter of the pipe 351 so that the outer circumference of the communication pipe 351 can be clamped when the motor case 311 and the speed reducer case 312 are brought into contact with each other in the axial direction. Holes 352 and 353 are formed.

As shown in FIGS. 10A and 10B, the communication pipe 351 is routed in the lubricating oil reservoir 15 a at a position below the lubricating oil supply port 260 and the two guide portions 110 and 120. The communication pipe 351 is substantially U-shaped when viewed from the axial direction as shown in FIG. 10B, avoiding interference with both the lubricant guide portions 330 and 340 and the driven gear 42. As shown in FIG. 11 (b), even when viewed from above, it is bent and arranged in a U shape.
Note that the communication pipe 351 has a bracket 351b provided at an intermediate portion thereof attached to the motor case 11 with a bolt 351c.

  Further, in the third embodiment, only the lower catch portion 340 on the side farther in the radial direction from the rotation center axis Cmot of the electric motor 3 among the lower catch portions 330 and 340 is implemented via the communication path 350. It is connected to a lubricating oil supply port 260 having the same shape as in the second embodiment.

That is, as shown in FIG. 11, in a layout where the motor chamber 14 protrudes toward the speed reducer chamber 15 and the lower catch portion 330 and the lubricating oil supply port 260 do not overlap in the axial direction, a space for communicating both is secured. Difficult to do. In this case, only the lower catch portion 340 on the outer diameter direction side of the electric motor 30 that easily secures a space for forming the communication passage 350 communicates with the lubricating oil port 260.
Therefore, the lower catch portion 330 is connected to the lubricating oil supply port 260 via the communication pipe 351, the lower catch portion 340, and the communication passage 350.

(Operation of Embodiment 3)
Next, the operation of the third embodiment will be described.
In the third embodiment, the communication pipe 351 is assembled in advance in the motor case 311 as shown in FIG. That is, the upper end portion of the communication pipe 351 is held in the motor case 311 using the bracket 351b in a state where the upper end portion of the communication pipe 351 is fitted to the semicircular arcs of both pipe clamping notches 332b and 342b.

  In this state, the motor case 311 and the speed reducer case 312 are abutted in the axial direction, so that both upper ends of the communication pipe 351 are sandwiched between the pipe clamping notches 331b, 341b, 332b, 342b. It is fixed with. At this time, it is preferable that a sealing material is interposed between the communication pipe 351 and the pipe clamping notches 331b, 341b, 332b, and 342b.

In the third embodiment configured as described above, both lower catch portions 330 and 340 are always communicated by the communication pipe 351. For this reason, even if the lubricating oil falls on only one of the lower catch portions 330 and 340 due to the difference between the forward and backward movement of the vehicle, the oil level of the lower catch portions 330 and 340 is always constant. Can be equalized.
Further, the supply of the lubricating oil to the lubricating oil supply port 260 is performed only from one lower catch portion 340. Therefore, even when the oil level of the lower catch portion 340 is lowered by the suction force on the through shaft center oil passage 47 side, the oil level height with the other lower catch portion 330 is made uniform through the communication pipe 351. Can be planned.

(Effect of Embodiment 3)
In addition to the effects 1) to 8) described above, the electric drive device according to the third embodiment has the effects listed below.
3-1) The electric drive device of Embodiment 3 is
The lower catch portions 330 and 340 are directly connected to each other by a communication pipe 351 separately from the communication path 350.
Accordingly, the lower catch portions 330 and 340 are always communicated by the communication pipe 351, and compared with the case where this communication is not performed, the oil level height in both the lower catch portions 330 and 340 is equalized and stabilized. Lubricating oil can be supplied.
In addition, since the lower catch portions 330 and 340 are communicated by the communication pipe 351, the dimensional restriction on the unit case 1 side can be reduced as compared with the case where this communication is performed by the communication path formed in the unit case 1. Design flexibility is increased. In addition, the unit case 1 can be downsized.

  Furthermore, in Embodiment 3, since the communication pipe 351 is routed in the lubricating oil reservoir 15a of the reduction gear chamber 15, for example, it is compared with that routed in the motor chamber 14 which is a dry space. Thus, even if lubricating oil leaks in the communication pipe 351, it is difficult to leak outside.

3-2) The electric drive device of Embodiment 3 is
The electric drive device characterized in that the communication pipe 351 is routed through the axial position of the driven gear 42 below the lubricating oil supply port 260.
Accordingly, it is possible to reduce the size of the communication pipe 351 by reducing the dimension in the axial direction of the drive unit as the electric drive device. In particular, in the third embodiment, since the inside of the lubricating oil reservoir 15a is routed, the space of the reduction gear chamber 15 can be used effectively.

3-3) The electric drive device of Embodiment 3 is
The unit case 1 is divided into a motor case 311 arranged in the outer diameter direction of the electric motor 3 and a speed reducer case 312 arranged in the outer diameter direction of the speed reduction mechanism 4 in the axial direction.
The bottom portions of the lower catch portions 330 and 340 are formed as bottom plate portions 332a and 342a as first catch portion forming portions formed in the motor case 311 and second catch portion forming portions formed in the speed reducer case 312. Bottom plate portions 331a and 341a of
Pipe clamping notch parts 331b, 341b as pipe clamping parts for clamping the communication pipe 351 in the axial direction when the bottom plate parts 332a, 342a and the bottom plate parts 331a, 341a are abutted in the axial direction. 332b and 342b are provided.
Therefore, when the motor case 311 and the reduction gear case 312 are brought into contact with each other as the unit case 1 is assembled, the upper end portion of the communication pipe 351 is sandwiched and fixed by the pipe clamping notch portions 331b, 341b, 332b, 342b. The
Therefore, the fixing work of the independent communication pipe 351 becomes unnecessary, and the assembling workability is excellent.
Furthermore, by interposing a sealing material between the communication pipe 351 and the pipe clamping notches 331b, 341b, 332b, 342b, leakage of lubricating oil from both lower catch portions 330, 340 is suppressed, and efficient lubricating oil is obtained. Can be supplied.

3-4) The electric drive device of Embodiment 3 is
Of the lower catch portions 330 and 340, only the lower catch portion 340 that is farther in the radial direction from the rotation center axis Cmot of the electric motor 3 is connected to the lubricating oil supply port 260 through the communication path 350. And
Therefore, the axial distance between the motor chamber 14 and the reduction gear chamber 15 is shortened by an amount that does not form a communication path between the lower catch portion 330 and the lubricating oil supply port 260 on the side closer to the rotation center axis Cmot of the electric motor 3. The axial dimension of the drive unit can be shortened.
In this case, the communication between the lower catch portion 330 and the lubricating oil supply port 260 can be ensured by the communication between the lower communication passages 330 and 340 through the communication pipe 351.

(Embodiment 4)
FIG. 12 shows an electric drive device according to the fourth embodiment.
The fourth embodiment is a modification of the third embodiment, and is an example in which the communication pipe 451 is connected to the positions of the motor side catch portions 332 and 342 of the motor case 311.
In this example, the communication pipe 451 is inserted into the pipe insertion holes 452 and 453 formed in the motor side catch portions 332 and 342 in a circular shape.

  Therefore, even in the fourth embodiment, the effects of 3-1), 3-2) and 3-4) can be obtained.

  As mentioned above, although the electric drive device of the present invention has been described based on the embodiment, the specific configuration is not limited to this embodiment, and the gist of the invention according to each claim of the claims As long as they do not deviate, design changes and additions are permitted.

  For example, in the embodiment, an example is shown in which the electric drive device is applied to an in-wheel motor type drive unit that drives the front wheels of the vehicle, but the present invention can also be applied to an electric drive device used for industrial equipment other than the vehicle. is there. Moreover, even when applied to a vehicle, the invention is not limited to the in-wheel motor type, and can be applied to an electric drive device that transmits rotation between the left and right wheels via a differential. In addition, the drive wheels can be applied to wheels other than the front wheels.

  In the embodiment, the speed reduction mechanism is provided with a planetary gear train in addition to the parallel shaft gear train. However, if the parallel shaft gear train is provided, the speed reduction mechanism without the planetary gear train is provided. Can also be used.

  Further, in the embodiment, when the lubricating oil guide portion is provided in the case, the example using the cylindrical portion for supporting the internal gear that supports the ring gear of the planetary gear mechanism is shown. However, the guide portion is not limited thereto. May be provided independently in the case. That is, when the speed reduction mechanism has no planetary gear mechanism as described above, the lubricating oil guide portion is provided independently in the case. Even if the speed reduction mechanism has a planetary gear mechanism, if the outer diameter of the ring gear and the driven gear are different, the lubricating oil guide portion is provided separately from the cylindrical portion for supporting the internal gear. May be.

  Further, in the embodiment, the lubricating oil guide portion is provided not only in the outer diameter direction of the driven gear, but also along the side surface, but at least as long as it is provided along the outer diameter direction of the driven gear. The desired effect can be obtained. In addition, when the lubricating oil guide portion is also provided on the side surface of the driven gear, the ring gear is also used as the side guide on the side where the planetary gear mechanism is provided in the axial direction with respect to the driven gear. Without limitation, the lubricating oil guide member may have an L-shaped cross-sectional shape on this side as well. In particular, when the planetary gear mechanism is not adjacent to the driven gear, it is preferable to form both end portions of the lubricating oil guide portion in the direction orthogonal to the axis in an L-shaped cross-sectional shape.

  Moreover, although the example which provided the catch part in the horizontal direction of the direction orthogonal to the rotation center axis | shaft of a driven shaft was shown in embodiment, you may provide in any one. In this case, it is preferable to provide it on the side where a lot of lubricating oil drops when the vehicle travels forward. Further, when applied to industrial equipment and the like, when the rotation direction of the motor is a fixed direction, it is preferably provided on the side where a lot of lubricating oil falls due to the rotation.

  In the embodiment, the ring gear is fixed to the support cylindrical portion of the case. In the embodiment, the projection is formed on the ring gear and the engagement groove is formed on the support cylindrical portion. The relationship with the groove may be reversed. Furthermore, as a fixing | fixed part, as shown in embodiment, it is not limited to the engaging groove and convex line | wire which were arrange | positioned in the circumferential shape. For example, it is also possible to use other structures such as inserting a non-rotating pin into the radial hole or recess provided in the ring gear from the support cylinder part side.

DESCRIPTION OF SYMBOLS 1 Unit case 2 Unit output shaft 3 Electric motor 4 Reduction mechanism 11 Motor case 12 Reduction gear case 12b Internal gear support cylindrical part 12c Engaging groove (fixing part)
15a Lubricating oil reservoir 40 Parallel shaft gear train 41 Drive gear 42 Driven gear 43 Driven shaft 50 Planetary gear mechanism 54 Ring gear (internal gear)
54s Side (side guide)
110, 120 Lubricating oil guide portions 111a, 121a Outer peripheral guide portions 112a, 122a Outer peripheral guide portions 112b, 122b Side guide portions 130, 140 Lower catch portions 151, 152 Communication passage 160 Lubricating oil supply ports 230, 240 Lower catch portions 230e Part 260 Lubricating oil supply port 330, 340 Lower catch part 331a, 341a Bottom plate part (catch part forming part)
331b, 341b Pipe clamping notch 332a, 342a Bottom plate part (catch part forming part)
332b, 342b Pipe clamping notch

Claims (12)

An electric motor and a speed reduction mechanism that reduces the speed of rotation of the electric motor and transmits it to the output shaft are accommodated in the case, and the rotation of the speed reduction mechanism scrapes the lubricating oil in the lubricating oil reservoir in the case. An electric drive device designed to be raised,
The reduction mechanism includes a parallel shaft gear train including a drive gear rotated by the electric motor and a driven gear that meshes with the drive gear and rotates the lubricating oil,
The case is provided along the outer periphery of the driven gear via a gap capable of ascending the lubricant between the outer periphery of the driven gear and extends to a higher position than the oil level of the lubricant storage portion. An electric drive device characterized in that an existing lubricant guide portion is provided. The electric drive device according to claim 1,
The reduction mechanism includes a planetary gear mechanism that inputs rotation of the driven gear and transmits the rotation to the output shaft.
The case has a cylindrical shape along the outer periphery of the internal gear of the planetary gear mechanism, and is provided with a supporting cylindrical portion that supports the internal gear,
A fixing portion for fixing the internal gear to the supporting cylindrical portion is provided at a position between the supporting cylindrical portion and the internal gear and excluding an intermediate portion in the vertical direction.
The electric drive device characterized in that the lubricating oil guide portion is formed by an intermediate portion of the supporting cylindrical portion that does not have the fixing portion. In the electric drive device according to claim 1 or 2,
In the speed reducer chamber that houses the speed reduction mechanism of the case, a catch portion is provided for receiving the lubricating oil scraped up by the driven gear,
The electric drive device according to claim 1, wherein the lubricant guide portion and the catch portion are provided on at least one of both sides sandwiching the rotation center of the driven gear in a horizontal direction orthogonal to the rotation center of the driven gear. In the electric drive device according to claim 3,
The lubricating oil guide portion and the catch portion are provided on both sides of the rotation center of the driven gear in the horizontal direction on the side where the amount of falling lubricant oil is large when the vehicle is traveling forward in a vehicle-mounted state. Electric drive device. In the electric drive device according to claim 3,
The case includes a supply port that is provided coaxially with a rotation center of a driven shaft that supports the driven gear and rotates integrally with the driven gear, and supplies the lubricating oil to an oil passage in the driven shaft;
The lubricating oil guide part and the catch part are provided on both sides in the horizontal direction across the rotation center of the driven gear,
An electric drive device characterized in that each catch portion and the supply port communicate with each other through a communication path. In the electric drive device according to claim 5,
One of the catch portions on both sides is provided with a lower extension portion extending below the supply port along the lubricant guide portion,
An electric drive device characterized in that a communication path between the catch portion forming the lower extension portion and the supply port is connected to the lower extension portion. The electric drive device according to claim 6,
An electric drive device characterized in that a first communication path connected to the lower extension part and a second communication path connected to the catch part not provided with the lower extension part are arranged in a straight line. . In the electric drive device according to any one of claims 5 to 7,
The electric drive device characterized in that the catch portions are directly communicated by a communication pipe separately from the communication path. The electric drive device according to claim 8,
The electric drive device characterized in that the communication pipe is routed through an axial position of the driven gear below the supply port. In the electric drive device according to claim 8 or 9,
The case is formed by dividing it in the axial direction into a motor case arranged in the outer diameter direction of the electric motor and a reducer case arranged in the outer diameter direction of the reduction mechanism,
The bottom of the catch part is formed by abutting in the axial direction a first catch part forming part formed on the motor case and a second catch part forming part formed on the speed reducer case,
The first catch portion forming portion and the second catch portion forming portion are provided with a pipe sandwiching portion that sandwiches the communication pipe in the axial direction when both are abutted in the axial direction. Electric drive device. The electric drive device according to any one of claims 1 to 10,
The lubricating oil guide portion includes an outer peripheral guide portion provided so as to cover an outer diameter direction of the driven gear, and a side guide portion provided so as to cover a side surface of the driven gear. Electric drive device. The electric drive device according to claim 11, wherein
The electric drive device according to claim 1, wherein the side guide portion is configured by a side surface of a ring gear arranged in an axial direction of the driven gear.