JP5200910B2 - Lubricating oil supply device for power transmission device - Google Patents

Description

  The present invention relates to a lubricating oil supply device for a power transmission device, and more particularly to a vehicle having an internal combustion engine, a drive source different from the internal combustion engine, and a power transmission device that transmits the power of the internal combustion engine and the drive source to drive wheels. The present invention relates to a lubricating oil supply device for a power transmission device that is mounted and supplies lubricating oil to a lubricated portion of the power transmission device.

  As a means for supplying lubricating oil to each part of the power transmission device, a technique for pumping the lubricating oil by an oil pump (pressure feeding means) is known. For example, Patent Document 1 discloses a power transmission device in which oil sucked by an oil pump is supplied to a first gear housing portion.

JP 2008-89134 A

  In a vehicle having an internal combustion engine, a drive source different from the internal combustion engine, and a power transmission device for transmitting the power of the internal combustion engine and the drive source to the drive wheels, a pressure feeding means for supplying lubricating oil to a lubricated portion of the power transmission device However, when the engine is operated by the power of the internal combustion engine, the supply amount of the lubricating oil may be reduced depending on the operation state of the internal combustion engine. For example, when a vehicle equipped with a power transmission device is a vehicle capable of traveling with power from a driving source different from that of the internal combustion engine by stopping rotation of the internal combustion engine, the internal combustion engine is stopped during traveling. Then, since the pumping means is also stopped, the supply of the lubricating oil to the lubricated part is stopped.

  In a vehicle including a power transmission device that transmits power of an internal combustion engine and power of a drive source different from the internal combustion engine to drive wheels, even when the internal combustion engine is stopped during traveling, lubricating oil is applied to the lubricated portion. It is hoped that it can be supplied.

  An object of the present invention is to have an internal combustion engine, a drive source different from the internal combustion engine, a power transmission device that transmits the power of the internal combustion engine and the drive source to drive wheels, and drive by stopping the rotation of the internal combustion engine When the internal combustion engine is stopped during traveling in a lubricating oil supply device of a power transmission device that is mounted on a vehicle that can travel with the power of the source and supplies lubricating oil to the lubricated part of the power transmission device Even so, an object of the present invention is to provide a lubricating oil supply device for a power transmission device capable of supplying lubricating oil to a lubricated portion.

The lubricating oil supply device of the power transmission device of the present invention has an internal combustion engine, a drive source different from the internal combustion engine, and a power transmission device that transmits the power of the internal combustion engine and the drive source to drive wheels, And a lubricating oil supply of a power transmission device that is mounted on a vehicle capable of running with the power of the drive source while stopping the rotation of the internal combustion engine, and that supplies the lubricating oil to the lubricated portion of the power transmission device A device for housing the portion to be lubricated and storing lubricating oil; a pumping means that operates by power of the internal combustion engine and pumps the stored lubricating oil; and a discharge from the pumping means A first passage for guiding the lubricant to be lubricated to the portion to be lubricated, an oil receiving portion that is disposed in the case and stores lubricating oil, a second passage that connects the oil receiving portion and the first passage And the oil receiving portion is Wherein the serial first passage is provided in a vertical direction above the outlet for outflow of lubricating oil to the lubricated portions, compared suction side of the flow path cross-sectional area of the lubricating oil and in the pumping unit, said first The sum of the channel cross-sectional area on the downstream side in the flow direction of the lubricating oil and the channel cross-sectional area of the second passage is larger than the connection portion with the second passage in the passage .

  In the lubricating oil supply device of the power transmission device of the present invention, a rotating member that is disposed in the case and rotates in conjunction with traveling of the vehicle, and is formed vertically below the rotating member in the case, And a storage part for storing lubricating oil, wherein the lubricating oil sent out from the storage part by rotation of the rotating member flows into the oil receiving part.

  In the lubricating oil supply device for a power transmission device according to the present invention, the drive source includes a rotating electrical machine, the oil receiving portion has an opening connected to the second passage, and the rotating electrical machine. An outflow port through which lubricating oil flows is formed, and the opening and the outflow port face each other.

  In the lubricating oil supply device for a power transmission device according to the present invention, the lubricated portion is a power transmission mechanism connected to a shaft that transmits the power of the internal combustion engine to the pressure feeding means.

  A lubricating oil supply device for a power transmission device according to the present invention includes an internal combustion engine, a drive source different from the internal combustion engine, a power transmission device that transmits the power of the internal combustion engine and the drive source to drive wheels, and the internal combustion engine. A lubricating oil supply device for a power transmission device that is mounted on a vehicle that can run with the power of a drive source while stopping rotation of the power transmission device and that supplies lubricating oil to a lubricated portion of the power transmission device. A case for storing the lubricating part and storing the lubricating oil, a pumping means that is operated by the power of the internal combustion engine and pumps the stored lubricating oil, and the lubricating oil discharged from the pumping means is guided to the lubricated part. A first passage, an oil receiving portion that is disposed in the case and stores lubricating oil, and a second passage that connects the oil receiving portion and the first passage are provided. The oil receiving part is provided vertically above the discharge port through which the lubricating oil flows out to the lubricated part in the first passage.

Thus, when the internal combustion engine is stopped, the lubricating oil stored in the oil receiving portion flows from the second passage into the first passage and is supplied from the discharge port to the lubricated portion. Therefore, according to the lubricating oil supply device of the power transmission device of the present invention, it is possible to supply the lubricating oil to the lubricated portion even when the internal combustion engine is stopped during traveling.
In addition, compared with the flow passage cross-sectional area on the suction side of the lubricating oil in the pumping means, the flow passage cross-sectional area on the downstream side in the flow direction of the lubricating oil relative to the connection portion with the second passage in the first passage, The sum with the channel cross-sectional area of the passage is large. Therefore, the pressure rise in the pressure feeding means is suppressed.

  Hereinafter, an embodiment of a lubricating oil supply device for a power transmission device of the present invention will be described in detail with reference to the drawings.

(Embodiment)
The embodiment will be described with reference to FIGS. 1 to 6. The present embodiment is mounted on a vehicle having an internal combustion engine, a drive source different from the internal combustion engine, and a power transmission device that transmits the power of the internal combustion engine and the drive source to drive wheels. The present invention relates to a lubricating oil supply device for a power transmission device that supplies lubricating oil.

  The lubricating oil supply device of the power transmission device of this embodiment supplies lubricating oil to the transmission (T / M) of the hybrid vehicle. The power transmission device (see reference numeral 1 in FIG. 1) is an oil supply that supplies lubricating oil that has been lifted up by a final ring gear (rotating member, see reference numeral 108 in FIG. 1) to an oil receiving portion (see reference numeral 40 in FIG. 1). And a lubrication mechanism for a shaft (see reference numerals 14 and 72 in FIG. 1) by an oil pump (see reference numeral 50 in FIG. 1). The input shaft 14 is formed with a communication hole (discharge port, see reference numeral 14b in FIG. 1) for supplying lubricating oil to the planetary gear (see reference numeral 82 in FIG. 1). The pump drive shaft 72 is formed with a communication hole for supplying lubricating oil to the planetary gear 84 (discharge port, see reference numeral 72b in FIG. 1).

  Since the oil pump 50 is driven by the engine (see symbol E in FIG. 1), the oil pump 50 cannot supply the lubricating oil to the planetary gears 82 and 84 when the engine E is stopped.

  On the other hand, in this embodiment, the discharge port of the oil pump 50 is connected to the connection passage (second passage, reference numeral 70 in FIG. 1) that is a route to the oil receiving portion 40 and the shafts 14 and 72. It is branched into a supply passage (see reference numeral 72a in FIG. 1) which is a route. The oil receiving portion 40 includes a communication hole 14b of the input shaft 14 through which lubricating oil flows out to a composite gear (see reference numeral 80 in FIG. 1), which is a necessary lubrication site (a portion to be lubricated), and a communication hole 72b of the pump drive shaft 72. Is also provided vertically above. By connecting the oil receiving portion 40 and the communication holes 14b and 72b arranged so as to have a water head difference via the connection passage 70, oil supply promotion to the oil receiving portion 40 during operation of the engine E, It is possible to supply oil to the planetary gears 82 and 84 during EV traveling.

  FIG. 1 is a cross-sectional view showing a structure of a power transmission device 1 to which an embodiment of a lubricating oil supply device for a power transmission device is applied. The power transmission device 1 is a power transmission device for a hybrid vehicle, and includes a motor generator MG1 (rotary electric machine), a motor generator MG2 (rotary electric machine), and a composite gear (power transmission mechanism) 80. Power transmission device 1 transmits the power of engine (internal combustion engine) E and the power of motor generators MG1 and MG2 as drive sources different from engine E to drive wheels (not shown) of the vehicle. As the engine E, an internal combustion engine, specifically, a gasoline engine, a diesel engine, an LPG engine, a methanol engine, a hydrogen engine, or the like can be used.

  Motor generator MG1 and motor generator MG2 have a function (power running function) as an electric motor driven by the supply of electric power and a function (regeneration function) as a generator that converts mechanical energy into electric energy. As motor generator MG1 and motor generator MG2, for example, a permanent magnet type AC synchronous motor generator can be used. As a power supply device that supplies power to motor generator MG1 and motor generator MG2, a power storage device such as a battery or a capacitor, a known fuel cell, or the like can be used. Motor generator MG1 uses engine power to start engine E. After the engine is started, the motor generator MG1 can function as a generator by the power of the engine E, and the generated power can be charged in the power supply device.

  Motor generator MG1 includes a rotor (rotor) 24 and a stator 16. The stator 16 is fixed to the case 8. The rotor 24 has a hollow shaft 30. An input shaft 14 that transmits the rotation of the engine E is passed through the hollow shaft 30. The shaft 30 is provided so as to be rotatable relative to the input shaft 14. The rotation of the engine E is transmitted from the output shaft 3 of the engine E to the input shaft 14 via the transaxle damper 13.

  The shaft 30 is rotatably supported by the case 8 via a ball bearing 34. The space for housing motor generator MG1 and the space for housing compound gear 80 and motor generator MG2 are partitioned by partition wall 7. A ball bearing 36 is provided between the partition wall 7 and the shaft 30. The shaft 30 is rotatably supported by the partition wall 7 via a ball bearing 36.

  Motor generator MG2 operates as a motor that is driven mainly by electric power and generates driving force of wheels. However, motor generator MG2 can function as a generator that collects electric power by performing regenerative braking during braking.

  Motor generator MG <b> 2 includes a rotor (rotor) 48 and a stator 46. The stator 46 is fixed to the case 4. A lid 2 is attached to the case 4. The rotor 48 has a hollow shaft 60. The shaft 60 is rotatably supported by a ball bearing 64 attached to the lid 2 and a ball bearing 66 attached to the partition wall. A pump drive shaft 72 for transmitting the rotation of the engine E to the oil pump 50 passes through a hollow portion of the shaft 60. The pump drive shaft 72 is provided to be rotatable relative to the shaft 60. The end of the pump drive shaft 72 on the engine E side is spline-fitted with the end of the input shaft 14 opposite to the engine E side, and the pump drive shaft 72 and the input shaft 14 rotate integrally.

  Compound gear 80 includes a planetary gear 84 that is a reduction gear that decelerates rotation of motor generator MG2, and a planetary gear 82 that operates as a power split device that splits power between engine E and motor generators MG1 and MG2. The planetary gear 82 and the planetary gear 84 are disposed coaxially and face each other in the axial direction.

  Planetary gear 84 includes a sun gear 92 that is spline-fitted with shaft 60, a pinion gear 88 that meshes with sun gear 92, and a planetary carrier 90 that supports the rotation shaft of pinion gear 88. The sun gear 92 is spline-fitted to an end portion of the shaft 60 on the output shaft 3 side in the axial direction, and rotates integrally with the shaft 60. A plurality of pinion gears 88 are arranged along the circumferential direction on the outer peripheral side of the sun gear 92. Planetary carrier 90 is fixed to the case and cannot rotate.

  The planetary gear 82 includes a sun gear 96 that is spline-fitted with the shaft 30, a pinion gear 98 that meshes with the sun gear 96, and a planetary carrier 100 that supports the rotation shaft of the pinion gear 98. The sun gear 96 is spline-fitted to an end portion of the shaft 30 opposite to the output shaft 3 side in the axial direction, and rotates integrally with the shaft 30. A plurality of pinion gears 98 are arranged along the circumferential direction on the outer peripheral side of the sun gear 96. Planetary carrier 100 is fixed to input shaft 14 that transmits the rotation of engine E, and rotates integrally with input shaft 14.

  The composite gear 80 has a counter drive gear 86. The counter drive gear 86 faces the pinion gear 88 of the planetary gear 84 and the pinion gear 98 of the planetary gear 82 in the radial direction. A ring gear 91 that meshes with the pinion gear 88 and a ring gear 99 that meshes with the pinion gear 98 are engraved on the inner peripheral portion of the counter drive gear 86. Further, a gear that meshes with the counter driven gear 106 is engraved on the outer periphery of the counter drive gear 86. Thus, the planetary gear 82 and the planetary gear 84 constitute a composite gear 80 in which the ring gear 91 and the ring gear 99 rotate together. The power transmitted from each of the pinion gears 88 and 98 is transmitted to the counter driven gear 106 via the counter drive gear 86.

  The counter driven gear 106 is connected to one side of the counter shaft 102 in the axial direction. A final drive pinion gear 104 is formed on the other side of the counter shaft 102 in the axial direction. The power transmitted to the counter driven gear 106 is transmitted to the final ring gear 108 via the counter shaft 102 and the final drive pinion gear 104. The power transmitted to the final ring gear 108 is transmitted to driving wheels of the vehicle via a differential mechanism (not shown).

  The hybrid vehicle according to the present embodiment is configured to be capable of EV traveling in which the rotation of the engine E is stopped and the vehicle is driven by the power of the motor generator MG2. During EV travel, the power of motor generator MG2 is transmitted from counter drive gear 86 to counter driven gear 106 via planetary gear 84, and the vehicle is driven.

  During EV travel, the operation of the engine E is stopped, and no power is generated by the motor generator MG1, and the sun gear 96 is in a free state. As a result, the input shaft 14 and the planetary carrier 100 connected to the output shaft 3 of the engine E stop rotating, and the sun gear 96 idles in the direction opposite to the rotation direction of the counter drive gear 86. The pinion gear 98 does not revolve, but only rotates. That is, during EV travel, the rotation of the input shaft 14 and the pump drive shaft 72 stops, so the oil pump 50 also stops.

  Next, a method for supplying lubricating oil in the power transmission device 1 will be described. The power transmission device 1 includes an oil pump 50, and lubricating oil fed by the oil pump 50 is supplied to the composite gear 80. The oil pump 50 is operated by the power of the engine E and pumps the lubricating oil stored in the case 4. The power of the engine E is transmitted to the oil pump 50 via the output shaft 3, the input shaft 14, and the pump drive shaft 72. FIG. 2 is an enlarged view of the vicinity of the oil pump 50 in FIG.

  The oil pump 50 is a known trochoid pump, and includes a drive rotor 51, a driven rotor 52, a rotor chamber 53, a suction port 54, a discharge port 55, and a pump cover 56. The drive rotor 51 is connected to the end of the pump drive shaft 72 opposite to the engine E side, and rotates integrally with the pump drive shaft 72. A rotor chamber 53 is formed in the lid 2. The rotor chamber 53 is formed at the end of the lid 2 opposite to the engine E side, and the pump cover 56 closes the opening of the rotor chamber 53 opposite to the engine E side. In the rotor chamber 53, the drive rotor 51 and the driven rotor 52 are disposed in an engaged state. The suction port 54 is connected to a lubricating oil storage location of the power transmission device 1 through a suction passage 57 and a strainer (not shown). The said storage location can be the storage part 29 mentioned later, for example.

  When the pump drive shaft 72 rotates with the operation of the engine E, the drive rotor 51 and the driven rotor 52 rotate, and the lubricating oil is sucked into the rotor chamber 53 from the suction port 54. The lubricating oil sucked into the rotor chamber 53 is pressurized by the drive rotor 51 and the driven rotor 52 and discharged to the discharge port 55. Lubricating oil discharged to the discharge port 55 flows toward the engine E through a supply passage 72a formed in the pump drive shaft 72 in the axial direction. The supply passage 72a penetrates the pump drive shaft 72 in the axial direction.

  As shown in FIG. 1, the input shaft 14 is formed with an axial oil passage 14 a formed in the axial direction. In the fitting portion between the input shaft 14 and the pump drive shaft 72, the supply passage 72a and the axial oil passage 14a are connected. The input shaft 14 is formed with a communication hole 14b that communicates the axial oil passage 14a and the radially outer side of the input shaft 14 in the radial direction. Centrifugal force acts on the lubricating oil in the axial oil passage 14 a as the input shaft 14 rotates. As a result, the lubricating oil flows out from the axial oil passage 14a to the planetary gear 82 through the communication hole 14b. When the rotation of the input shaft 14 is stopped, the lubricating oil flows out from the axial oil passage 14a to the planetary gear 82 through the communication hole 14b due to gravity or hydraulic pressure.

  The shaft 60 is formed with a radial communication hole 60 a for supplying lubricating oil to the planetary gear 84. In the pump drive shaft 72, a communication hole 72b is formed at a position corresponding to the communication hole 60a. The communication hole 72b communicates the supply passage 72a and the radially outer side of the pump drive shaft 72 in the radial direction. A part of the lubricating oil flowing through the supply passage 72a is supplied to the planetary gear 84 by the centrifugal force through the communication hole 72b and the communication hole 60a. When the rotation of the pump drive shaft 72 is stopped, the lubricating oil is supplied to the planetary gear 84 through the communication hole 72b and the communication hole 60a by gravity or hydraulic pressure.

  By supplying lubricating oil to the planetary gears 82 and 84 from the inside in the radial direction, the gears 96, 98, and 99 of the planetary gear 82 and the gears 92, 88, and 91 of the planetary gear 84 are efficiently lubricated. be able to. Further, according to the pressure feeding system using the oil pump 50, the lubricating oil can be supplied to the planetary gears 82 and 84 at an early stage when the vehicle starts to travel. For example, supply of lubricating oil to the planetary gears 82 and 84 is started at a low speed stage after the start of traveling.

  Furthermore, in the power transmission device 1, as will be described below with reference to FIG. 3, the lubricating oil that has been lifted up by the final ring gear 108 that rotates in conjunction with the traveling of the vehicle is supplied to each part. FIG. 3 is a cross-sectional view of the power transmission device 1 in the radial direction.

  A lubricating oil reservoir 29 is formed in the case 4 below the final ring gear 108 in the vertical direction. The final ring gear 108 rotates in the rotation direction (counterclockwise) indicated by reference numeral A5 in FIG. The rotation direction in the present embodiment indicates the rotation direction when the vehicle moves forward. Reference numerals A3 and A6 indicate the rotation directions of the input shaft 14 and the counter shaft 102, respectively. Due to the rotation of the final ring gear 108, the lubricating oil stored in the storage unit 29 is sent out (squeezed up) from the storage unit 29 and flows upward in the vertical direction as indicated by an arrow Y1. An oil receiving portion 40 is formed in the upper portion of the case 4 in the vertical direction. The oil receiver 40 is a lubricating oil tank disposed vertically above the counter drive gear 86, the counter driven gear 106, and the final ring gear 108, and stores the lubricating oil sent out by the final ring gear 108. The lubricating oil sent out by the final ring gear 108 flows into the oil receiver 40 (arrows Y2 and Y3) and is stored in the oil receiver 40.

  As shown in FIG. 1, the position of the oil receiving portion 40 corresponds to the position of the final ring gear 108 in the axial direction of the power transmission device 1. That is, the oil receiving portion 40 is disposed at a position where the lubricating oil delivered by the final ring gear 108 can reach. The side wall 41 on the engine E side in the axial direction of the oil receiving portion 40 is configured by the case 8, and the side wall 42 on the side opposite to the engine E side is configured by the case 4. Further, the bottom of the oil receiving portion 40 is constituted by a rib 43 formed on the case 4. The rib 43 protrudes from the case 4 toward the engine E side, and the tip end is in contact with the case 8.

  An outlet 41 a is formed in the side wall 41 on the engine E side. The lubricating oil stored in the oil receiving part 40 flows out toward each part of the power transmission device 1 through the outlet 41a. The lubricating oil stored in the oil receiver 40 is supplied to, for example, the motor generators MG1, MG2, the counter shaft 102, and the like.

  Thus, in the power transmission device 1, the lubricating oil is supplied to each part by the scraping method using the final ring gear 108 and the pressure feeding method using the oil pump 50. Here, depending on the operating condition of the engine E, the supply amount of the lubricating oil to the lubricated part may be reduced. For example, during EV travel in which the engine E is stopped and the vehicle is driven by the driving force of the motor generators MG1 and MG2, the oil pump 50 is stopped as the engine E is stopped. Thereby, the pumping of the lubricating oil toward the composite gear 80 is stopped, and the supply of the lubricating oil to the composite gear 80 is stopped.

  In contrast, in the present embodiment, a connection passage that connects the discharge port of the oil pump 50 and the oil receiver 40 is provided, and when the engine E is stopped, the lubricating oil in the oil receiver 40 is connected to the connection passage. And flows into the discharge port. Thereby, the lubricating oil can be supplied to the composite gear 80 even when the engine E is stopped.

  As shown in FIG. 2, a connection passage 70 is connected to the discharge port 55. The end of the connection passage 70 opposite to the discharge port 55 side is connected to the oil receiver 40. As shown in FIG. 1, an inflow port (opening) 42 a is formed in a side wall 42 opposite to the engine E side in the oil receiving portion 40. The connection passage 70 is connected to the inflow port 42a. That is, the connection passage 70 is a passage for lubricating oil that connects the discharge port 55 of the oil pump 50 and the inlet 42 a of the oil receiving portion 40.

  FIG. 4 is a view for explaining the relationship between the discharge port 55 and the communication holes 14b and 72b and the inflow port 42a.

  As shown in FIG. 4, the inlet 42 a of the oil receiver 40 is provided at a position vertically above the discharge port 55, the input shaft 14, and the pump drive shaft 72 of the oil pump 50. That is, the oil receiving part 40 is provided above the communication holes 14b and 72b in the vertical direction. Here, the oil receiving portion 40 is provided vertically above the communication holes 14b and 72b. That is, at least a part of the oil receiving portion 40 is positioned above the communication holes 14b and 72b in the vertical direction. In other words, the oil level of the lubricating oil stored in the oil receiving portion 40 is positioned above the communication holes 14b and 72b in the vertical direction. Note that the lower end of the oil receiving portion 40 is positioned vertically above the communication holes 14b and 72b, and the oil level of the lubricating oil stored in the oil receiving portion 40 is always vertically higher than the communication holes 14b and 72b. It is desirable to be in Since the oil receiving portion 40 is disposed vertically above the communication holes 14b and 72b, the lubricating oil can be supplied to the composite gear 80 during EV traveling, as will be described below.

  FIG. 2 shows the flow of the lubricating oil when the engine E is operated at a low speed. When the engine E is operated and the oil pump 50 is driven, the lubricating oil is discharged from the rotor chamber 53 to the discharge port 55. The lubricating oil discharged to the discharge port 55 is supplied to the composite gear 80 through the supply passage 72a. When the discharge pressure of the oil pump 50 is low, such as when the engine E is operated at a low speed, the lubricating oil discharged from the oil pump 50 is preferentially supplied to the composite gear 80. Since the inflow port 42a is above the discharge port 55 in the vertical direction, the discharge is performed while the discharge pressure of the oil pump 50 is lower than the hydraulic head difference (hydraulic pressure corresponding to the height difference) between the discharge port 55 and the inflow port 42a. There is no flow of lubricating oil from the port 55 toward the connection passage 70. That is, the lubricating oil discharged from the oil pump 50 is preferentially supplied to the composite gear 80 until the discharge pressure of the oil pump 50 exceeds the water head difference between the discharge port 55 and the inflow port 42a.

  FIG. 5 shows the flow of lubricating oil when the engine E is operated at a high speed. When the rotational speed of the engine E rises and the discharge pressure of the oil pump 50 exceeds the water head difference between the inlet 42a and the discharge port 55, the discharged lubricating oil flows into the connection passage 70 as shown by an arrow Y4. Is supplied to the oil receiver 40 via Part of the lubricating oil discharged from the oil pump 50 to the discharge port 55 flows through the connection passage 70 and flows into the oil receiving portion 40 through the inflow port 42a.

  As a result, not only the lubricating oil fed by the final ring gear 108 but also the lubricating oil fed by the oil pump 50 flows into the oil receiving portion 40. Corresponding to the increase in the amount of lubricating oil flowing into the oil receiving portion 40, the flow rate of the lubricating oil supplied from the oil receiving portion 40 to each part of the power transmission device 1 increases. For example, the cooling efficiency of motor generators MG1 and MG2 is improved by increasing the flow rate of lubricating oil supplied from oil receiver 40 to motor generators MG1 and MG2. When engine E is operated at a high speed, motor generators MG1 and MG2 are also operated at a high speed. In such a case, the amount of lubricating oil supplied to motor generators MG1 and MG2 increases, so that lubrication from oil receiver 40 to motor generators MG1 and MG2 corresponds to the amount of heat generated in motor generators MG1 and MG2. It is possible to appropriately increase or decrease the supply amount of oil.

  FIG. 6 is a diagram illustrating the flow of the lubricating oil when the engine E is stopped.

  When the engine E is stopped, the oil pump 50 is stopped. In this case, the lubricating oil in the oil receiving portion 40 is connected from the inflow port 42a as shown by the arrow Y5 due to the oil level of the lubricating oil stored in the oil receiving portion 40 and the water head difference between the communication holes 14b and 72b. It flows into the passage 70. The lubricating oil that has flowed into the connection passage 70 is supplied to the composite gear 80 through the discharge port 55, the supply passage 72a, and the communication holes 14b and 72b. That is, the lubricating oil can be supplied to the composite gear 80 even during EV travel when the engine E is stopped. Even when the engine E is stopped, since the final ring gear 108 continues to scrape the lubricating oil to the oil receiving portion 40, the lubricating oil is stably supplied from the oil receiving portion 40 to the composite gear 80. Is done.

  Considering the introduction of the plug-in hybrid system and the like, it is conceivable that EV travel time in the hybrid vehicle will increase in the future. Therefore, supply of lubricating oil to the composite gear 80 when the engine E is stopped becomes a problem. According to the lubricating oil supply device of the power transmission device of the present embodiment, if the vehicle is traveling and the final ring gear 108 is rotating, the lubricating oil can be supplied to the composite gear 80 even during EV traveling. it can. Thereby, even if the EV running time increases, it is possible to continuously supply the lubricating oil to the composite gear 80.

  Further, as will be described below, in the oil pump 50 of the present embodiment, the pipe resistance on the discharge side is smaller than that on the suction side. Thereby, the pressure rise in the oil pump 50 does not occur, and the relief valve can be eliminated. In the conventional oil supply system using an oil pump, it has been difficult to increase the cross-sectional area of the supply passage 72a. For this reason, the conventional oil pump has a problem that the flow passage cross-sectional area of the discharge portion is smaller than the flow passage cross-sectional area of the suction passage 57, and the internal pressure in the oil pump increases. As a result, a relief valve has become indispensable for the oil pump, and the size of the oil pump has become large.

  In the present embodiment, in the oil pump 50, the sum of the cross-sectional area A2 of the connection passage 70 and the cross-sectional area A3 of the supply passage 72a is larger than the cross-sectional area A1 of the suction passage 57. Here, each cross-sectional area A1, A2, A3 is a flow path cross-sectional area (cross-sectional area of a cross section orthogonal to the axial direction of each passage). In other words, compared with the cross-sectional area of the oil pump 50 on the suction side of the lubricating oil, the connection in the first passage (discharge port 55 and supply passage 72a) that guides the lubricating oil discharged from the oil pump 50 to the lubricated portion. The sum of the flow passage cross-sectional area on the downstream side in the flow direction of the lubricating oil and the flow passage cross-sectional area of the connection passage 70 is larger than the connection portion (discharge port 55) with the passage 70. As described above, since the sum of the cross-sectional areas on the discharge side is set to be larger than the sum of the cross-sectional areas on the suction side, no pressure increase occurs in the oil pump 50. For this reason, a relief valve can be abolished, and the physique of the oil pump 50 can be reduced compared with the conventional one.

  In addition, the outlet 41a and the inlet 42a are arranged so that the efficiency of discharging the lubricating oil from the oil receiver 40 is improved. Specifically, as shown in FIGS. 1 and 3, the outlet 41a and the inlet 42a are arranged at positions facing each other. In other words, the outlet 41a is formed on the downstream side of the inlet 42a in the flow direction of the lubricating oil that is pumped to the oil pump 50 and flows into the oil receiver 40 from the inlet 42a.

  Due to the energy of the flow of the lubricating oil flowing into the oil receiving portion 40 from the inlet 42a, the lubricating oil flows toward the outlet 41a in the oil receiving portion 40. Thereby, the discharge efficiency of the lubricating oil from the oil receiving part 40 increases. Further, as the rotational speed of the engine E increases, the discharge pressure of the oil pump 50 increases, so that the flow velocity of the lubricating oil flowing into the oil receiving portion 40 from the inlet 42a increases. Thereby, the flow of the lubricating oil toward the outflow port 41a is promoted, and the flow velocity of the lubricating oil flowing out from the outflow port 41a is increased. As a result, a turbulent state and a collision jet flow are realized in the flow of the lubricating oil flowing out from the outlet 41a, and the cooling efficiency of the motor generators MG1 and MG2 is increased. Therefore, motor generators MG1 and MG2 can be efficiently cooled at the time of high-speed traveling where both engine E and motor generators MG1 and MG2 are operated at a high speed.

  In the present embodiment, the oil receiving portion 40 that stores the lubricating oil sent out by the final ring gear 108 also serves as a container for the lubricating oil connected to the discharge port 55, but instead of this, the discharge port 55 And a lubricating oil container connected to each other may be provided independently. In this case, when the engine E is operated and the discharge pressure of the oil pump 50 is high, the lubricating oil discharged from the oil pump 50 flows into the container and is stored. On the other hand, during EV travel, the lubricating oil stored in the container flows out of the container and is supplied to the composite gear 80 via the connection passage 70 and the supply passage 72a.

It is sectional drawing which shows the structure of the power transmission device with which embodiment of the lubricating oil supply apparatus of the power transmission device of this invention was applied. It is an enlarged view of the oil pump vicinity in embodiment of the lubricating oil supply apparatus of the power transmission device of this invention. It is sectional drawing of the radial direction of the power transmission device with which embodiment of the lubricating oil supply apparatus of the power transmission device of this invention was applied. It is a figure for demonstrating the relationship between the discharge port of the embodiment of the lubricating oil supply apparatus of the power transmission device of this invention, a communicating hole, and an inflow port. It is a figure which shows the flow of lubricating oil when the engine is drive | operated by high rotation in embodiment of the lubricating oil supply apparatus of the power transmission device of this invention. It is a figure which shows the flow of the lubricating oil at the time of the engine stop in embodiment of the lubricating oil supply apparatus of the power transmission device of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Power transmission device 2 Lid 3 Output shaft 4,8 Case 14 Input shaft 14a Axial oil path 14b Communication hole 16 Stator 24 Rotor 30 Shaft 40 Oil receiving part 41, 42 Side wall 41a Outlet 42a Inlet 43 Rib 46 Stator 48 Rotor 50 Oil pump 54 Suction port 55 Discharge port 57 Suction passage 60 Shaft 60a Communication hole 70 Connection passage 72 Pump drive shaft 72a Supply passage 72b Communication hole 80 Compound gear 82, 84 Planetary gear 86 Counter drive gear 88, 98 Pinion gear 90, 100 Planetary carrier 91,99 Ring gear 92,96 Sun gear 108 Final ring gear E Engine MG1, MG2 Motor generator

Claims (4)

An internal combustion engine; a drive source different from the internal combustion engine; a power transmission device that transmits the internal combustion engine and power of the drive source to drive wheels; and the rotation of the internal combustion engine is stopped to drive the drive source A lubricating oil supply device for a power transmission device that is mounted on a vehicle capable of traveling with the power of the power supply and that supplies lubricating oil to the lubricated portion of the power transmission device,
A case for storing the lubricated part and storing lubricating oil;
A pumping means that operates by the power of the internal combustion engine and pumps the stored lubricating oil;
A first passage for guiding lubricating oil discharged from the pressure feeding means to the lubricated portion;
An oil receiving portion disposed in the case and storing lubricating oil;
A second passage connecting the oil receiving portion and the first passage;
The oil receiving portion is provided vertically above a discharge port through which lubricating oil flows out to the lubricated portion in the first passage ,
Compared with the flow passage cross-sectional area on the suction side of the lubricating oil in the pumping means, the flow passage cross-sectional area on the downstream side in the flow direction of the lubricating oil with respect to the connection portion with the second passage in the first passage, A lubricating oil supply device for a power transmission device, wherein the sum of the flow passage cross-sectional area of the second passage is large . The lubricating oil supply device for a power transmission device according to claim 1,
A rotating member disposed in the case and rotating in conjunction with the traveling of the vehicle;
A vertical portion lower than the rotating member in the case, and a storage section for storing lubricating oil;
The lubricating oil supply device for a power transmission device, wherein the lubricating oil sent out from the storage portion by the rotation of the rotating member flows into the oil receiving portion. The lubricating oil supply device for a power transmission device according to claim 2,
The drive source includes a rotating electric machine,
The oil receiving portion is formed with an opening to which the second passage is connected and an outlet through which lubricating oil flows toward the rotating electrical machine. The opening and the outlet are mutually connected. A lubricating oil supply device for a power transmission device, characterized by facing each other. In the lubricating oil supply apparatus of the power transmission device according to any one of claims 1 to 3 ,
The lubricated part is a power transmission mechanism connected to a shaft that transmits the power of the internal combustion engine to the pumping means.

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