JP2010001945A - Lubricating structure of driving device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To surely supply lubricating oil to a lubrication required part of a motor driving gear and in its vicinity existing in an elevated spot even in long time-low speed operation in which lubrication easily becomes insufficient. <P>SOLUTION: A driving motor and a driving motor shaft 20 for transmitting output of the driving motor are arranged in a casing sealed with the lubricating oil. A front wheel differential 11 is arranged under the driving motor shaft 20. Reduction gear pairs are arranged via first and second intermediate shafts 23 and 27 between the driving motor shaft 20 and a differential case 11a of the front wheel differential 11. A first driving gear 20a (a motor driving gear) is arranged on the driving motor shaft 20 as the reduction gear pairs. A first driven gear 23a meshing with the first driving gear 20a is arranged on the first intermediate shaft 23, and a second driven gear 27a is arranged on the second intermediate shaft 27. A lower part of these first and second driven gears 23a and 27a is respectively surrounded by first and second intermediate baffle members 52 and 55, and the lubricating oil is stored in these first and second intermediate baffle members 52 and 55. <P>COPYRIGHT: (C)2010,JPO&INPIT

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, 2. Description of the Related Art There is known a lubrication structure for a drive device that includes a reduction gear pair provided between a drive motor shaft and a differential case via an intermediate shaft in a casing sealed with lubricating oil.

For example, the lubrication structure for a drive device of a hybrid electric vehicle disclosed in Patent Document 1 includes an internal gear pump (hydraulic pump) that is rotated by an output shaft, and the internal gear pump lubricates a lubrication required portion in the drive device. It has become.
JP-A-7-76229

  However, in the conventional lubrication structure of the driving device, the hydraulic pump, by its nature, cannot suck up and discharge the lower lubricating oil unless it is rotated at a certain rotational speed. There was a problem that the number of rotations of the pump was insufficient and the lubricating oil could not be sufficiently supplied to the lubrication required portion of the drive device.

  The present invention has been made in view of the above points, and an object of the present invention is to provide a motor drive gear at a high place and the vicinity of the motor drive gear at a high place even during long-time low-speed operation where lubrication tends to be insufficient. The purpose is to reliably supply lubricating oil to the lubrication site.

  In order to achieve the above object, according to the present invention, a baffle member that surrounds a lower portion of a driven gear driven by a drive motor and accumulates lubricating oil is provided.

  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 lubrication structure for a drive device is provided which includes a reduction gear pair provided between the drive motor shaft and the differential case via an intermediate shaft in a casing sealed with lubricating oil.

And the reduction gear pair is
A motor drive gear provided on the drive motor shaft;
A driven gear provided on the intermediate shaft that meshes with the motor drive gear,
An intermediate baffle member that surrounds the lower portion of the driven gear and accumulates lubricating oil is provided.

  According to the above configuration, if the lubricating oil is accumulated in the intermediate baffle member surrounding the driven gear of the intermediate shaft by scraping up the differential ring gear provided in the differential case at the time of high rotation or sucking up the hydraulic pump provided separately, Even at low rotations where the lifting action of the differential ring gear and the suction action by the hydraulic pump are insufficient, the driven gear lifts up the lubricant accumulated in the intermediate baffle member, and the drive motor shaft at a high location and its vicinity To supply. For this reason, the poor lubrication at the time of long-time low-speed driving | running | working of the lubrication required part in a high place is prevented.

In the second invention, in the first invention,
A drive gear provided on the intermediate shaft;
A differential ring gear provided in the differential case meshing with the drive gear;
A lower baffle member surrounding the lower portion of the differential ring gear and storing lubricating oil.

  According to the above configuration, the lubricating oil in the lower baffle member is lifted up by the diff ring gear at high rotation, the lubricating oil is replenished in the upper intermediate baffle member, and the driven gear scrapes the lubricating oil in the intermediate baffle member. The frying further improves the lubrication of the high drive motor shaft and its vicinity.

In the third invention, in the second invention,
The intermediate shaft includes a first intermediate shaft and a second intermediate shaft,
A first driven gear provided on the first intermediate shaft and driven by the motor drive gear;
A second driven gear provided on the second intermediate shaft and driven by the drive gear of the first intermediate shaft;
A first intermediate baffle member is provided at a lower portion of the first driven gear;
A second intermediate baffle member is provided below the second driven gear.

  According to said structure, when a drive device has two intermediate shafts, lubrication of the whole drive device is carried out by replenishing lubricating oil from the bottom to the top in order of a lower baffle member, a 2nd intermediate baffle member, and a 1st intermediate baffle member. Is improved.

In the fourth invention, in the third invention,
A unit casing for storing the drive motor and the differential;
The unit casing is formed of a first casing and a second casing coupled in the axial direction of the drive motor,
The first intermediate baffle member is attached to one of the first casing and the second casing on the side close to the first driven gear,
The second intermediate baffle member is attached to the other of the first casing and the second casing.

  According to said structure, the assembly | attachment of the 1st and 2nd intermediate baffle member surrounding the lower part of each driven gear can be performed easily.

  As described above, according to the present invention, the intermediate baffle member is provided so as to surround the lower portion of the driven gear on the intermediate shaft, and the lubricant accumulated in the intermediate baffle member is swept up by the driven gear. Thus, even during long-time low-speed operation where lubrication tends to be insufficient, the lubricating oil can be reliably supplied to the motor drive gear at a high place and the necessary lubrication site in the vicinity thereof.

  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 is on the opposite side of the engine 2 from the engine-side unit casing 17 as a first casing on the engine side (right side as viewed from the passenger compartment) coupled in the axial direction of the output shaft 2 a of the engine 2. It is formed with an anti-engine side unit casing 18 as a second casing, 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 for driving the generator 5 and the drive motor 3, and is configured to supply electric power to the generator 5 and 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 that stores lubricating oil that is sealed in the unit casing 16 and lubricates the entire drive device 15 is formed in the lower portion of the differential case 11a. The engine side of the differential ring gear 11b and the differential case 11a is surrounded by a lower baffle member 51. The lubricating oil in the lower baffle member 51 stored in the differential lubricating oil reservoir 40 is swept up by the differential ring gear 11b. The lower baffle member 51 is, for example, a sheet metal member and is attached to the engine-side unit casing 17 with bolts or the like.

  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 lower portion of the first driven gear 23 a is surrounded by the first intermediate baffle member 52. The first intermediate baffle member 52 is, for example, a sheet metal member, and is fastened to a first boss portion 53 provided on the non-engine-side unit casing 18 by a bolt 54. Similarly, the lower portion of the second driven gear 27 a is surrounded by the second intermediate baffle member 55. The second intermediate baffle member 55 is, for example, in the form of a sheet metal, and is fastened by a bolt 54 to a second boss portion 56 provided in the engine side unit casing 17.

  As shown by white arrows in FIGS. 5 and 6, the lubricating oil scraped up by the diff ring gear 11 b is stored in the lubricating oil reservoir 41 and the first and second intermediate baffle members 52 and 55. ing.

  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. Further, the first driven gear 23 a scoops up the lubricating oil accumulated in the first intermediate baffle member 52.

  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. Further, the second driven gear 27 a scoops up the lubricating oil accumulated in the second intermediate baffle member 55.

  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. When the differential ring gear 11b is driven, the lubricating oil in the lower baffle member 51 accumulated in the differential lubricating oil reservoir 40 is swept up, and the lubricating oil is applied to the first and second intermediate baffle members 52 and 55 in the upper part. Is replenished. 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 stored in the lubricating oil reservoir 41 and the first and second intermediate baffle members 52 and 55 provided in the vicinity of the first drive gear 20a by the differential ring gear 11b and the hydraulic pump 42 at the time of high rotation. And the second driven gears 23a and 27a scoop up the lubricating oil collected in the first and second intermediate baffle members 52 and 55, and the parking gear 20b scoops up the lubricating oil stored in the lubricating oil reservoir 41. Since the lubricating oil is supplied to the first drive gear 20a located in the high place and the vicinity thereof, the poor lubrication in the vicinity of the first drive gear 20a does not occur 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.

  When the driving device 15 has the first and second intermediate shafts 23, 27, the diff ring gear 11b lifts the lubricating oil of the lower baffle member 51 during high rotation, and the first and second driven gears 23a, 27a The lubricating oil in the first and second intermediate baffle members 52 and 55 is lifted up. In this way, by replenishing the lubricating oil from the bottom to the top in the order of the lower baffle member 51, the second intermediate baffle member 55, and the first intermediate baffle member 52, the lubrication of the entire drive device 15 can be improved.

  Further, the first intermediate baffle member 52 is attached to the non-engine side unit casing 18 on the side close to the first driven gear 23a, and the second intermediate baffle member 55 is attached to the engine side unit casing 17 close to the second driven gear 27a. Thus, the first and second intermediate baffle members 52 and 55 can be easily assembled.

  Therefore, according to the lubricating structure of the drive device 15 of the hybrid electric vehicle according to the present embodiment, the first and second intermediate baffle members 52 and 55 are moved on the first and second intermediate shafts 23 and 27, respectively. Provided so as to surround the lower portions of the gears 23a and 27a, and the lubricating oil accumulated in the first and second intermediate baffle members 52 and 55 is swept up by the first and second driven gears 23a and 27a, respectively. Thus, even during low-speed operation for a long time when lubrication is likely to be insufficient, the lubricating oil can be reliably supplied to the first drive gear 20a at a high place and the necessary lubrication site in the vicinity thereof.

(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 the above embodiment, the lower baffle member 51, the first intermediate baffle member 52, and the second intermediate baffle member 55 are made of sheet metal, but are formed by ribs protruding from the engine side unit casing 17 and the anti-engine side unit casing 18. May be.

  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. It is the perspective view which opened the non-engine side unit casing and made the baffle member visible.

Explanation of symbols

3 drive motor 11 front wheel differential 11a differential case 11b differential ring gear 15 drive unit 16 unit casing 17 engine side unit casing (first casing)
18 Anti-engine side unit casing (second casing)
20 drive motor shaft 20a first drive gear (motor drive gear)
23 1st intermediate shaft 23a 1st driven gear 23b 2nd drive gear 27 2nd intermediate shaft 27a 2nd driven gear 27b 3rd drive gear 51 Lower baffle member 52 1st intermediate baffle member 55 2nd intermediate baffle member

Claims (4)

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 drive device lubrication structure comprising a reduction gear pair provided via an intermediate shaft between the drive motor shaft and the differential case in a casing sealed with lubricating oil,
The reduction gear pair is
A motor drive gear provided on the drive motor shaft;
A driven gear provided on the intermediate shaft that meshes with the motor drive gear,
An lubrication structure for a drive device, characterized in that an intermediate baffle member is provided surrounding the lower portion of the driven gear and storing lubricating oil. In the lubricating structure of the drive device according to claim 1,
A drive gear provided on the intermediate shaft;
A differential ring gear provided in the differential case meshing with the drive gear;
And a lower baffle member surrounding the lower portion of the diff ring gear and storing lubricating oil. In the lubricating structure of the drive device according to claim 2,
The intermediate shaft is composed of a first intermediate shaft and a second intermediate shaft,
A first driven gear provided on the first intermediate shaft and driven by the motor drive gear;
A second driven gear provided on the second intermediate shaft and driven by the drive gear of the first intermediate shaft;
A first intermediate baffle member is provided at a lower portion of the first driven gear;
A lubrication structure for a driving device, wherein a second intermediate baffle member is provided below the second driven gear. In the lubricating structure of the drive device according to claim 3,
A unit casing for storing the drive motor and the differential;
The unit casing is formed of a first casing and a second casing coupled in the axial direction of the drive motor,
The first intermediate baffle member is attached to one of the first casing and the second casing on the side close to the first driven gear,
The lubrication structure for a drive device, wherein the second intermediate baffle member is attached to the other of the first casing and the second casing.

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