JP5146136B2 - Lubrication structure of drive unit - Google Patents

Description

  The present invention relates to a lubrication structure for a drive device including a drive motor such as a hybrid electric vehicle.

  Conventionally, a drive motor, a drive motor shaft that transmits the output of the drive motor, a differential (differential gear, differential device) provided below the drive motor shaft, a differential case provided in the differential, A differential lubricating oil reservoir provided at a lower portion of the differential case; and a plurality of reduction gear pairs provided via an intermediate shaft between the drive motor shaft and the differential case; and the drive motor shaft and its vicinity 2. Description of the Related Art Lubricating structures for driving devices that supply lubricating oil to the motor are known.

For example, Patent Document 1 discloses a lubricating structure for a drive device for a hybrid electric vehicle. This lubricating device includes an electric oil pump, and the electric oil pump is used to supply lubricating oil to a lubrication required portion in the drive device.
JP 2007-321927 A

  However, in the lubrication structure of the driving device of Patent Document 1, since an electric oil pump is provided separately, the number of parts is increased by that amount, and the cost is increased, and electric energy is consumed only for supplying lubricating oil. There was a problem to do.

  The present invention has been made in view of such points, and an object of the present invention is to reliably supply lubricating oil into the driving device while suppressing an increase in the number of parts and consumption of electric energy.

  In order to achieve the above object, in the present invention, a hydraulic pump is provided on an intermediate shaft having a pair of reduction gears extending from the drive motor shaft to the differential case.

  Specifically, in the first invention, a drive motor, a drive motor shaft that transmits the output of the drive motor, a differential provided below the drive motor shaft, a differential case provided on the differential, A differential lubricating oil reservoir provided at a lower portion of the differential case; and a plurality of reduction gear pairs provided via an intermediate shaft between the drive motor shaft and the differential case; and the drive motor shaft and its vicinity The lubrication structure of the drive device that supplies the lubricating oil to the target is intended.

The lubrication structure of the driving device includes a hydraulic pump that supplies the lubricating oil from the differential lubricating oil reservoir to the driving motor shaft and the vicinity thereof,
The hydraulic pump is provided at the end of the intermediate shaft and is driven by the rotation of the intermediate shaft ,
A through passage is formed in the intermediate shaft,
As a part of the oil passage between the hydraulic pump and the drive motor shaft and the vicinity thereof, the through passage is used,
A detour pipe line passing through the inside of the casing wall from a portion of the casing where the end opposite to the hydraulic pump of the intermediate shaft is supported is provided,
The detour pipe is used as a part of the oil path between the hydraulic pump and the drive motor shaft and the vicinity thereof .

  According to the above configuration, without adding an electric pump or the like, the lubricating oil stored in the differential lubricating oil reservoir is sucked up by the hydraulic pump using the rotation of the intermediate shaft, and the drive motor shaft and the upper part of the differential The vicinity is lubricated. For this reason, cost increase and electric energy consumption are prevented. In addition, the hydraulic pump uses a rotation of an intermediate shaft that has a lower rotation speed than the drive motor shaft and a higher rotation speed than the differential rotation shaft. In addition to being prevented, there is no case where the rotational speed is insufficient during normal operation and the lubricating oil cannot be sucked up sufficiently.

In addition, according to the above configuration, the lubricating oil can be passed to the opposite side with a simple configuration of providing a through hole in the intermediate shaft, so there is no need to provide a separate pipe, etc. Does not require space.

Furthermore, according to said structure, if it is the wall of a casing, it will be easy to form a detour pipe line in an appropriate position.

In the second invention, in the first invention,
A one-way clutch is provided between the hydraulic pump and the intermediate shaft to prevent pump drive in the reverse flow direction.

  According to the above configuration, when the intermediate shaft rotates in reverse, such as when moving backward, the hydraulic pump is not driven by the one-way clutch. There is no.

In the third invention, in the first or second invention,
Between the drive motor shaft and the differential case, a three-stage reduction gear pair is provided in order via a first intermediate shaft and a second intermediate shaft,
The hydraulic pump is configured to be driven by the rotation of the second intermediate shaft.

According to the above configuration, when a three-stage reduction gear pair is provided, by using the rotation of the second intermediate shaft that is moderately decelerated close to the differential side, instead of the first intermediate shaft that is not sufficiently decelerated The hydraulic pump is rotated at a more appropriate rotational speed .

  As described above, according to the present invention, a hydraulic pump that supplies lubricating oil from the differential lubricating oil reservoir to the drive motor shaft and the vicinity thereof is provided at the end of the intermediate shaft, and this hydraulic pump is driven by the rotation of the intermediate shaft. By doing so, it is possible to reliably supply the lubricating oil into the driving device while suppressing an increase in the number of parts and consumption of electric energy.

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

-Configuration of hybrid electric vehicle-
FIG. 1 is a schematic configuration diagram of a hybrid electric vehicle 1 according to an embodiment of the present invention. The hybrid electric vehicle 1 includes an engine 2 and a drive motor 3 as power sources. The engine 2 is used only for power generation, and all the power for moving the automobile 1 depends on the drive motor 3. That is, the vehicle 1 is a so-called series hybrid electric vehicle, and includes a high-voltage battery 4 and a generator 5 driven by the engine 2 in addition to the engine 2 and the drive motor 3.

  The engine 2 is composed of, for example, a hydrogen rotary engine, and is stored in gasoline fuel tank 6 and hydrogen fuel tank 7 as used fuel, and hydrogen with less exhaust emission when the catalyst is inactive than gasoline. And can be switched. The engine 2 is mounted in the engine room in the vehicle width direction (sideways). Although not shown in detail, the output shaft 2 a of the engine 2 is directly connected to the rotating shaft of the generator 5 on the same axis. For this reason, when the engine 2 rotates, the rotating shaft of the generator 5 rotates at the same rotational speed, and electric energy is generated in the generator 5.

  On the other hand, the drive motor 3 is connected to the front wheel 10 via a differential gear (front wheel differential 11).

  As shown in FIGS. 2 to 6, the drive device 15 includes a unit casing 16 that houses the generator 5, the drive motor 3, and the front wheel differential 11. The unit casing 16 includes an engine side unit casing 17 on the engine side (right side when viewed from the vehicle interior) coupled in the axial direction of the output shaft 2 a of the engine 2 and an anti-engine side unit casing on the opposite side of the engine 2. 18, and both are connected by a connecting bolt 19. The drive motor 3 and the generator 5 are accommodated in the non-engine-side unit casing 18 so that the output shaft 3a of the drive motor 3 and the rotating shaft 5a of the generator 5 (shown only in FIG. 4) are in parallel. . Since the drive motor 3 and the generator 5 are fitted in the engine direction with respect to the non-engine-side unit casing 18, positioning and assembly are easy. Moreover, the engine side of the engine side unit casing 17 can be opened and closed by a lid portion 17e for the purpose of assembly and maintenance.

  In the present embodiment, the outer diameter of the generator 5 and the outer diameter of the drive motor 3 are substantially the same, but since this is a series hybrid electric vehicle, the drive motor is the sum of the output of the generator 5 and the output of the battery 4. For example, if the maximum output of the generator 5 is 80 kW, the maximum output of the drive motor 3 is 120 kW. For this reason, the maximum rotational speed of the drive motor 3 is about twice the maximum rotational speed of the generator 5.

  As shown in FIGS. 5 to 7, the output shaft 3 a of the drive motor 3 is spline-coupled to the drive motor shaft 20 that transmits the output in an integral manner. The drive motor shaft 20 is supported by a first ball bearing 21 on the side opposite to the engine side unit casing 18 and a second ball bearing 22 on the side of the engine side unit casing 17. A first drive gear 20a as a motor drive gear is integrally formed between the first and second ball bearings 21 and 22 of the drive motor shaft 20. A parking gear 20b is spline-coupled to the engine side of the drive motor shaft 20 from the second ball bearing 22, that is, on the side opposite to the drive motor 3 of the first drive gear 20a. The drive motor shaft 20 is formed in a hollow shape in the axial direction, and its tip is sealed with a cap 20c so that lubricating oil does not go back and forth inside the hollow, and a nut 20d is fastened to prevent the parking gear 20b from coming off. Since the parking gear 20b can be assembled to the drive motor shaft 20 from the side opposite to the drive motor 3 with the lid portion 17e removed, assembly is facilitated. Although not shown in detail, when the automobile 1 is parked, the parking gear 20b is locked by a locking mechanism 17f provided on the lid portion 17e side.

  A first intermediate shaft 23 is provided obliquely below the rear of the drive motor shaft 20. The first intermediate shaft 23 is supported by a first taper bearing 24 on the side opposite to the engine side unit casing 18 and a second taper bearing 25 on the side of the engine side unit casing 17. A first driven gear 23 a is formed integrally with the first intermediate shaft 23 on the non-engine side (left side). The first driven gear 23a is meshed so as to be driven by the first drive gear 20a. On the engine side of the first intermediate shaft 23, a second drive gear 23b is spline-coupled to rotate integrally.

  A second intermediate shaft 27 is provided below the first intermediate shaft 23. The second intermediate shaft 27 is supported by a third taper bearing 28 on the side opposite to the engine side unit casing 18 and a fourth taper bearing 29 on the side of the engine side unit casing 17. A second driven gear 27 a is integrally formed on the engine side of the second intermediate shaft 27. The second driven gear 27a is engaged with the second drive gear 23b so as to be driven. A third drive gear 27b is spline-coupled to the second intermediate shaft 27 on the non-engine side in a rotationally integrated manner.

  Although not shown in detail, the front wheel differential 11 includes a side gear, a pinion gear, and the like, and is covered with a differential case 11a. The differential case 11a is supported by a fifth taper bearing 30 on the side opposite to the engine side unit casing 18 and a sixth taper bearing 31 on the side of the engine side unit casing 17. A differential ring gear 11b is bolted to the engine side of the differential case 11a. The differential ring gear 11b is engaged with the third drive gear 27b so as to be driven. The right wheel drive shaft 32 is connected to the engine side of the differential case 11a, and the left wheel drive shaft 33 is connected to the non-engine side.

  As described above, the first drive gear 20a, the first driven gear 23a, the first driven gear 23a, the first driven gear 23a, and the first driven gear 23a are provided between the drive motor shaft 20 and the differential case 11a via the first intermediate shaft 23 and the second intermediate shaft 27. The second reduction gear pair includes a second drive gear 23b and a second driven gear 27a, and the third reduction gear pair includes a third reduction gear pair including a third drive gear 27b and a diff ring gear 11b. The reduction gear ratio (for example, 1.440) of the first reduction gear pair of the drive motor shaft 20 and the first intermediate shaft 23 is the reduction of the second reduction gear pair of the first intermediate shaft 23 and the second intermediate shaft 27. It is set smaller than the gear ratio (for example, 1.697).

  With this configuration, the generator 5 is disposed obliquely above and forward of the front wheel differential 11 in the engine room, and the drive motor 3 is disposed obliquely above and behind the generator 5. As shown in FIG. 3, the drive device 15 is arranged so that the oil pan 2 b and the unit casing 16 of the engine 2 are above the lowest ground clearance.

  On the other hand, as shown in FIG. 1, the battery 4 is configured to absorb the power generated by the generator 5 and supply the power to the drive motor 3. The battery 4 is connected to the generator 5 and the drive motor 3 via an AC-DC converter 8 as a first converter and a DC-AC converter 9 as a second converter, respectively. The AC-DC converter 8 and the DC-AC converter 9 are configured to control power transfer and conversion among the battery 4, the generator 5, and the drive motor 3. The AC-DC converter 8 and the DC-AC converter 9 are unitized as one inverter unit 35. As shown in FIG. 5, the inverter unit 35 is disposed above the generator 5 and in front of the drive motor 3. The battery 4 need not be provided in the engine room, and may be provided, for example, at the rear of the vehicle body.

-Lubrication structure of drive device-
Next, the lubrication structure of the drive device 15 will be described in detail.

  A differential lubricating oil reservoir 40 for storing lubricating oil for lubricating the entire drive device 15 is formed at the lower portion of the differential case 11a. The lubricating oil stored in the differential lubricating oil reservoir 40 is swept up by the differential ring gear 11b.

  Further, a hydraulic pump 42 is provided to supply the lubricating oil from the differential lubricating oil reservoir 40 to the lubricating oil reservoir 41 and further to the drive motor shaft 20 and the vicinity thereof.

  As shown in FIG. 6, the hydraulic pump 42 is provided at the opposite end of the second intermediate shaft 27 on the engine side. The hydraulic pump 42 is a trochoid pump that is driven by the rotation of the second intermediate shaft 27. Although not shown in detail, the hydraulic pump 42 has one more internal tooth than the external tooth. The external teeth are configured to perform a pumping action while rotating in the same direction. Since the relative speed between the inner teeth and the outer teeth is very small, tooth wear and noise are reduced. Further, a one-way clutch 44 is provided between the hydraulic pump 42 and the second intermediate shaft 27 for preventing pump drive in the reverse flow direction. A lubricating through passage 27 c is formed in the second intermediate shaft 27 so as to penetrate in the axial direction, and one end of the lubricating through passage 27 c communicates with the discharge side of the hydraulic pump 42.

  A first branching through hole 27d is formed between the one-way clutch 44 and the third taper bearing 28 in the lubricating through passage 27c. As indicated by an arrow in FIG. 6, the lubricating oil discharged from the first branch through hole 27d flows from the outer side of the third taper bearing 28 to the inner side, lubricates the third taper bearing 28, and then moves downward. It starts to flow. By utilizing the centrifugal force of the taper bearing, the action of sucking the lubricating oil from the outer side to the inner side is used.

  On the other hand, a bypass through-hole 17a is formed on the opposite side of the second intermediate shaft 27 in the engine-side unit casing 17 from the hydraulic pump 42. The engine side of the bypass through hole 17a is closed with a plug 17b. Lubricating oil passing through the lubricating through passage 27c is discharged from a gap 17c formed between the bypass through-hole 17a and the end of the second intermediate shaft 27, from the outer side to the inner side of the fourth taper bearing 29. After flowing in and lubricating the fourth taper bearing 29, it flows out downward. The lubricating oil flowing downward flows into the inner side from the outer side of the sixth taper bearing 31 through the through hole 17d formed in the boss-shaped portion of the engine side unit casing 17 that supports the sixth taper bearing 31. After the 6 taper bearing 31 is lubricated, it is stored in the differential lubricating oil storage section 40.

  The bypass through-hole 17 a communicates with a bypass duct 46 formed in the wall of the engine-side unit casing 17. Further, an oil chamber 47 for storing lubricating oil is formed above and obliquely behind the drive motor shaft 20. The bypass duct 46 extends upward and obliquely rearward from the bypass through-hole 17 a and communicates with the oil chamber 47 through a first communication hole 47 a formed in the rear wall portion forming the oil chamber 47.

  A second branch through hole 46a is formed behind the first intermediate shaft 23 in the bypass pipe 46, and lubricating oil passing through the bypass pipe 46 is discharged from the second branch through hole 46a. The taper bearing 25 flows from the outer side to the inner side, lubricates the second taper bearing 25, and then flows downward.

  As shown in FIGS. 8 and 9, the oil chamber 47 is formed across the engine-side unit casing 17 and the counter-engine-side unit casing 18. A second communication hole 47 b and a third communication hole 47 c are formed on the bottom surface forming the oil chamber 47. The second communication hole 47b is formed right above the second drive gear 23b, and the lubricating oil in the oil chamber 47 flows out to the second drive gear 23b. The third communication hole 47c is formed above the first drive gear 20a, and the lubricating oil in the oil chamber 47 flows out to the first drive gear 20a. A wall surface of the non-engine-side unit casing 18 forming the oil chamber 47 is formed with a fourth communication hole 47d so that the lubricating oil flows out to the output shaft 3a side of the drive motor 3 through the fourth communication hole 47d. It has become. The lubricating oil flowing out from the fourth communication hole 47d flows from the outer side of the first ball bearing 21 to the inner side, and after lubricating the first ball bearing 21, flows from the outer side to the inner side of the first taper bearing 24. The first taper bearing 24 is lubricated. A fifth communication hole 47e is formed in the engine side wall surface of the engine-side unit casing 17 forming the oil chamber 47, and the lubricating oil flowing out of the fifth communication hole 47e passes through the vicinity of the parking gear 20b to the second side. The ball bearing 22 flows from the outer side to the inner side to lubricate the second ball bearing 22. The lubricating oil is accumulated in a lubricating oil reservoir 41 formed in the vicinity of the first drive gear 20a, that is, below the parking gear 20b in the engine-side unit casing 17. The parking gear 20b serves as a lubricating oil lifting member that lifts the lubricating oil in the lubricating oil reservoir 41. The parking gear 20b supplies lubricating oil from the lubricating oil reservoir 41 to the first drive gear 20a, the first and second ball bearings 21, 22 and the like. In addition, if the left-right width of the lubricating oil reservoir 41 is reduced, the lifting effect is improved. The lubricating oil in the lubricating oil reservoir 41 is stored up to the height of the outer race of the second ball bearing 22. An air vent hole 47f is formed in the upper wall forming the oil chamber 47.

  The differential lubricating oil reservoir 40 is partly partitioned by the baffle plate 48 to prevent the differential ring gear 11b from rippled. An oil filter 49 is provided at the bottom of the differential lubricating oil reservoir 40 partitioned by the baffle plate 48, and the lubricating oil purified through the oil filter 49 is formed through the anti-engine side unit casing 18. Then, it passes through a suction pipe 50 extending upward to the hydraulic pump 42 and is sucked up by the hydraulic pump 42.

-Operation-
Next, the operation of the drive device 15 for the hybrid electric vehicle according to the present embodiment will be described.

  At the time of low-torque operation where the output torque required for the drive motor 3 is low, such as during low-speed operation of the automobile 1 or when the vehicle is started, the drive motor 3 is driven by electric power supplied from the battery 4 and during medium-torque operation. It is driven by electric power supplied from a generator 5 driven by the engine 2.

  On the other hand, the drive motor 3 is driven by electric power supplied from both the generator 5 and the battery 4 during high torque operation with high required torque, such as during sudden acceleration.

  The AC-DC converter 8 converts AC power into DC power, and the DC-AC converter 9 converts DC power into AC power whose frequency is controlled. When supplying power from the generator 5 to the drive motor 3, the AC power generated by the generator 5 is supplied to the AC-DC converter 8 and converted into DC power, and then again the DC-AC converter. 9 converts the DC power into AC power and supplies it to the drive motor 3.

  Further, when supplying power from the battery 4 to the drive motor 3, the DC power output from the battery 4 is converted into AC power of a predetermined frequency by the DC-AC converter 9 and supplied to the drive motor 3. Is done.

  Furthermore, when charging the battery 4, the AC power generated by the generator 5 is converted into DC power by the AC-DC converter 8 and supplied to the battery 4. The battery 4 is charged by supplying the generated power from the generator 5 and the regenerative power from the drive motor 3.

  When the amount of power stored in the battery 4 is small, the generator 5 is operated by operating the engine 2 so that the generator 5 generates more power than the power required to drive the drive motor 3 with the required torque. At the same time, the difference between the power generated by the generator 5 and the required power of the drive motor 3 is supplied to the battery 4 for charging.

  Next, transmission of the output of the drive motor 3 and supply of lubricating oil will be described.

  The output of the drive motor 3 transmitted to the drive motor shaft 20 is transmitted to the differential case 11a of the front-wheel differential 11 through a three-stage reduction gear pair.

  Specifically, when the drive motor shaft 20 is driven, the first drive gear 20a rotates and the first driven gear 23a of the first intermediate shaft 23 is driven. The first reduction gear pair reduces the first stage. At this time, the parking gear 20b scoops up the lubricating oil stored in the lubricating oil reservoir 41. In this manner, the lubricating oil in the lubricating oil reservoir 41 is lifted up by the existing parking gear 20b without separately providing a dedicated lifting member. Since the parking gear 20b is provided on the drive motor shaft 20 before the rotational torque is increased by being decelerated until reaching the front wheel differential 11, there is no need to increase the tooth width. The lubricating oil in 41 is not lifted more than necessary, and the rotational resistance of the drive motor shaft does not increase.

  Next, the second drive gear 23 b of the first intermediate shaft 23 drives the second driven gear 27 a of the second intermediate shaft 27. The second speed reduction gear pair reduces the second stage.

  At this time, the hydraulic pump 42 is driven by driving the second intermediate shaft 27 and sucks up the lubricating oil stored in the differential lubricating oil storage section 40 through the suction pipe 50. Thus, by using the rotation of the second intermediate shaft 27 moderately decelerated close to the front wheel differential 11 side instead of the first intermediate shaft 23 which is not sufficiently decelerated, the drive motor shaft The rotational speed is smaller than 20 and the rotational speed of the front wheel differential 11 is larger than that of the rotation shaft of the front wheel differential 11. The cavitation due to high speed is prevented, and the rotational speed is insufficient during normal operation. Can't be sucked up enough.

  Next, the sucked lubricating oil is discharged from the hydraulic pump 42 and flows out from the first branching through hole 27d and the gap 17c while passing through the lubricating through passage 27c. At this time, the lubricating oil can be passed to the opposite side with a simple configuration using the lubricating through-passage 27c of the second intermediate shaft 27, so there is no need to provide a separate pipe or the like, increasing the number of parts and extra space. Never do.

  Next, a part of the lubricating oil flows out from the second branch through hole 46 a while passing through the bypass duct 46, and the rest reaches the oil chamber 47 from the first communication hole 47 a. The lubricating oil in the oil chamber 47 flows out from the second communication hole 47b, the third communication hole 47c, the fourth communication hole 47d, and the fifth communication hole 47e, and lubricates each lubricated portion. In this way, since the lubricating oil is passed through the lubricating oil conduit that bypasses the inside of the wall of the unit casing 16, the bypass conduit 46 can be disposed at an appropriate position.

  Next, the third drive gear 27b of the second intermediate shaft 27 drives the diff ring gear 11b. At this time, the third stage of deceleration is performed. By driving the differential ring gear 11b, the lubricating oil stored in the differential lubricating oil storage section 40 is lifted up. By combining the lifting action of the lubricating oil by the differential ring gear 11b and the suction action by the hydraulic pump 42, the lubrication required portion in the unit casing 16 is sufficiently lubricated.

  On the other hand, when the drive motor 3 is driven at a low speed for a long time, the lifting action of the lubricating oil by the differential ring gear 11b and the sucking action by the hydraulic pump 42 are not sufficiently exhibited. However, the lubricating oil is accumulated in the lubricating oil reservoir 41 provided in the vicinity of the first drive gear 20a by the diff ring gear 11b and the hydraulic pump 42 at the time of high rotation, and the accumulated lubricating oil is increased by the parking gear 20b. The first drive gear 20a located in the vicinity of the first drive gear 20a and the vicinity thereof is prevented from causing poor lubrication near the first drive gear 20a even during low-speed operation.

  Thus, without adding an electric pump or the like, the lubricating oil stored in the differential lubricating oil storage unit 40 is sucked up by the hydraulic pump 42 using the rotation of the second intermediate shaft 27, and the upper portion of the front wheel differential 11. The drive motor shaft 20 and its vicinity are lubricated. For this reason, cost increase and electric energy consumption are prevented.

  When the second intermediate shaft 27 rotates reversely, such as when moving backward, the hydraulic pump 42 is not driven by the one-way clutch 44, so the hydraulic pump 42 does not reversely rotate and sucks the lubricating oil accumulated in the lubricating oil reservoir 41. .

  Thus, the output of the drive motor 3 is larger than the output of the generator 5, and the maximum rotational speed of the drive motor 3 is about twice the maximum rotational speed of the generator 5. Since the three-stage reduction is performed before reaching the differential case 11a, the gear diameter of each reduction gear pair is smaller than that of the two-stage reduction gear pair. For this reason, the drive device 15 does not swell rearward, and the whole becomes compact.

  Further, the magnitude ratio between the drive gear diameter and the driven gear diameter is smaller than that of the two-stage reduction gear pair. Furthermore, the second reduction gear pair of the first intermediate shaft 23 and the second intermediate shaft 27 whose speed reduction gear ratio of the first reduction gear pair of the drive motor shaft 20 and the first intermediate shaft 23 that becomes high rotation is reduced to low rotation. Therefore, the gear noise is effectively reduced.

  Further, the center of gravity of the entire drive device 15 can be lowered by providing the engine 2 having a large mass and the generator 5 connected to the engine 2 not in the upper part away from the front wheel differential 11 but in the diagonally upper front. Therefore, the roll of the drive device 15 is reduced. Furthermore, by arranging the drive motor 3 obliquely upward and rearward of the generator 5, the front wheel differential 11, the drive motor 3, the generator 5 and the engine 2 are arranged in a compact manner.

  Further, the unit casing 16 is divided in the axial direction into an engine side unit casing 17 and an anti-engine side unit casing 18 so that the drive motor 3 and the generator 5 are parallel to each other in the anti-engine side unit casing 18. The drive motor 3 and the generator 5 can be assembled very easily. Further, since the generator 5, the drive motor 3, and the front wheel differential 11 are housed in the unit casing 16 in a compact manner, the entire drive device 15 can be laid out more compactly.

  In addition, since the first intermediate shaft 23 is provided behind the vacant drive motor shaft 20 by providing the drive motor 3 obliquely above and behind the generator 5, the three-stage reduction gear pair is compact. Be placed.

  Furthermore, since the inverter unit 35 including the first and DC-AC converter 9 is provided in a free space above the generator 5 and in front of the drive motor 3, the drive unit 15 of the hybrid electric vehicle including the inverter unit 35 is provided. A compact layout is realized.

  Therefore, according to the lubricating structure of the drive device 15 of the hybrid electric vehicle according to the present embodiment, the hydraulic pump 42 that supplies the lubricating oil from the differential lubricating oil reservoir 40 to the driving motor shaft 20 and the vicinity thereof is connected to the second intermediate shaft 27. By providing the hydraulic pump 42 at the end and driving the second intermediate shaft 27 by rotation, the lubricating oil is reliably supplied into the driving device while suppressing an increase in the number of parts and consumption of electric energy. be able to.

(Other embodiments)
The present invention may be configured as follows with respect to the above embodiment.

  That is, in the said embodiment, although the engine 2 was made into the hydrogen rotary engine, it is not limited to this, A normal gasoline engine and a diesel engine may be sufficient.

  In the above-described embodiment, the drive device 15 includes the first intermediate shaft 23 and the second intermediate shaft 27 and the reduction gear pair includes three stages. However, the drive device 15 includes only one intermediate shaft and two reduction gear pairs. It may be composed of steps. In this case, a hydraulic pump may be provided on the intermediate shaft.

  In the above embodiment, a series hybrid electric vehicle is used, but a parallel hybrid electric vehicle may be used. In the above embodiment, the front wheel drive is used, but the rear wheel drive may be used. In this case, the differential is a rear wheel differential.

  In addition, the above embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or a use.

  As described above, the present invention is useful for a drive device for a front-wheel drive hybrid electric vehicle.

1 is a schematic configuration diagram of a hybrid electric vehicle according to an embodiment of the present invention. It is a perspective view which shows the drive device of a hybrid electric vehicle. It is a front view of the drive device of a hybrid electric vehicle. It is a perspective view of the drive device which removed the engine. It is a side view of the drive device which removed the non-engine side unit casing. FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. 5. It is a perspective view which shows the main components of a drive device. It is a perspective view which expands and shows the oil chamber of the non-engine side, and its periphery. It is the expansion perspective view which removed the cover part and made the 5th communicating hole visible.

3 drive motor 11 front wheel differential 11a differential case 11b differential ring gear 15 drive device 20 drive motor shaft 20a first drive gear 23 first intermediate shaft 23a first driven gear 23b second drive gear 27 second intermediate shaft 27a second driven gear 27b Third drive gear 40 Differential lubricating oil reservoir 42 Hydraulic pump 44 One-way clutch 46 Detour pipe

Claims (3)

A drive motor;
A drive motor shaft for transmitting the output of the drive motor;
A differential provided below the drive motor shaft;
A differential case provided in the differential;
A differential lubricating oil reservoir provided at a lower portion of the differential case;
A plurality of reduction gear pairs provided via intermediate shafts between the drive motor shaft and the differential case;
The drive motor shaft and a drive device lubrication structure for supplying lubricant to the vicinity thereof,
A hydraulic pump for supplying lubricating oil from the differential lubricating oil reservoir to the drive motor shaft and the vicinity thereof;
The hydraulic pump is provided at the end of the intermediate shaft and is driven by the rotation of the intermediate shaft ,
A through passage is formed in the intermediate shaft,
As a part of the oil passage between the hydraulic pump and the drive motor shaft and the vicinity thereof, the through passage is used,
A detour pipe line passing through the inside of the casing wall from a portion of the casing where the end opposite to the hydraulic pump of the intermediate shaft is supported is provided,
The lubrication structure for a drive device, wherein the bypass pipe is used as a part of an oil path between the hydraulic pump and the drive motor shaft and the vicinity thereof . In the lubricating structure of the drive device according to claim 1,
A lubrication structure for a drive device, wherein a one-way clutch is provided between the hydraulic pump and the intermediate shaft to prevent pump drive in the reverse flow direction. In the lubricating structure of the drive device according to claim 1 or 2,
Between the drive motor shaft and the differential case, a three-stage reduction gear pair is provided in order via a first intermediate shaft and a second intermediate shaft,
The lubrication structure for a driving device, wherein the hydraulic pump is driven by the rotation of the second intermediate shaft.

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