JP6200790B2 - Vehicle drive device - Google Patents

Description

  The present invention relates to a vehicle drive device, and more particularly, to a vehicle drive device capable of protecting an electrical coupling.

  Conventionally, in the vehicle drive device described in Patent Document 1, a pair of electric motors and a pair of planetary gear speed reducers are provided on the left and right sides of the case, and a hydraulic brake is provided between the electric motors. An electric oil pump is provided outside the case together with a lid member that closes the opening of the case. In addition, a valve member and a sensor are provided in the middle of an oil passage that supplies oil from the electric oil pump to each electric motor, each planetary gear type reduction gear, or a hydraulic brake. The valve member and the sensor are attached to the lid member. It is attached.

JP2013-13195A

  By the way, in the vehicle drive device described in Patent Document 1, a solenoid valve is provided as a valve member, and an electric coupling interposed on a wire for supplying a control signal and electric power to the solenoid valve is required. The electrical coupling is not specifically disclosed. It is desired that such an electric joint arranged outside the case be protected from external force such as stepping stones and water, and in particular, the valve member and sensor are designed with high liquid tightness. In the case of joints, liquid intrusion is not assumed and special consideration is required.

  This invention is made | formed in view of the said subject, The objective is to provide the drive device for vehicles which can protect an electric coupling from external forces, such as a stepping stone, and moisture.

In order to achieve the above object, the invention described in claim 1
On the power transmission path between the power source of the vehicle (for example, electric motors 2A and 2B in the embodiment described later), the wheels of the vehicle (for example, the left rear wheel LWr and the right rear wheel RWr in the embodiment described later) and the power source A housing (for example, a case 11 of the embodiment described later) that houses at least one of the power transmission mechanisms (for example, first and second planetary gear speed reducers 12A, 12B of the embodiment described later) When,
To-be-cooled parts of the power source (for example, to-be-cooled parts A1 and B1 in embodiments described later), to-be-lubricated parts (for example, to-be-lubricated parts A2 and B2 in embodiments to be described later), and to-be-cooled of the power transmission mechanism Liquid supply device (for example, in the embodiments described later) for supplying a liquid fluid to the cooled portion that is at least one of the portion and the lubricated portion (for example, the lubricated portions A3, B3 in the embodiments described later) Electric oil pump 70),
A vehicle drive device (for example, a rear wheel drive device 1 according to an embodiment described later),
The casing extends in a substantially horizontal direction from a side surface of the casing (for example, an outer wall surface 72b of a lid member 72 in an embodiment described later), and a flow path of the liquid fluid formed in the casing (for example, A flow in which an intermediate fluid passage (for example, an oil discharge passage 95 in an embodiment described later) is formed to communicate the first and second cooling channels 130A, 130B) in the embodiment described later and the liquid fluid supply device. It has a path forming part (for example, an extension part 72a of the lid member 72 of the embodiment described later),
The liquid fluid supply device extends substantially vertically above the flow path forming portion at an extending end portion of the flow path forming portion (for example, an end portion 72a1 of an extending portion 72a in an embodiment described later). Arranged to
The side surface of the housing, the upper surface of the flow path forming portion (for example, the upper surface 72a2 of an extension portion 72a in an embodiment described later), and the side surface of the liquid fluid supply device facing the side surface of the housing ( For example, in a space (for example, a space T in an embodiment described later) surrounded by an inner surface 70a) of an electric oil pump in an embodiment described later, an electric drive component installed in the housing or the liquid fluid supply Electrical joints (for example, couplers 87 and 88 in the embodiments described later) interposed on the electric wires (for example, electric wires 89a and 89b in the embodiments described later) for supplying an electrical signal or power to the apparatus are disposed,
The side surface of the liquid fluid supply device includes a first side surface (for example, a first side surface 70a1 of an embodiment described later) closer to the side surface of the housing, and a lower side than the first side surface and more than the first side surface. A second side surface (for example, a second side surface 70a2 of an embodiment described later) that is separated from the side surface of the housing,
The electrical coupling is arranged at a position facing the second side surface in the longitudinal direction of the vehicle.

Moreover, in addition to the structure of Claim 1, the invention of Claim 2 is
On the side surface of the housing, a pair of support devices (for example, mounts of the embodiments described later) for supporting the vehicle drive device on a skeleton member of the vehicle (for example, a subframe 13 of the embodiments described later). Members 13a, 13b) are attached,
The electrical coupling is characterized in that both sides are surrounded by the pair of support devices.

In addition to the configuration described in claim 1 or 2, the invention described in claim 3
The vehicle drive device is supported by a skeleton member of the vehicle,
The electrical joint is surrounded by the skeleton member.

Moreover, in addition to the structure in any one of Claims 1-3, the invention of Claim 4 is
The liquid fluid supply device is connected to an extension end of the flow path forming portion, extends in a substantially horizontal direction, and has a base (for example, a base 70b in an embodiment described later) on which the intermediate fluid flow path is formed. It is characterized by having.

According to the first aspect of the present invention, the electric coupling can be protected from external forces such as stepping stones from the front, rear and lower sides of the vehicle and from water.
In addition, the electrical coupling can be efficiently disposed by protecting the electrical coupling from an external force or water from above by the liquid fluid supply device, and effectively using the constrained space.

  According to the second aspect of the present invention, the electric coupling can be further protected from external forces such as stepping stones from the left and right sides of the vehicle and from water.

  According to the invention of claim 3, it is possible to further protect the electric coupling from external force such as a stepping stone from above the vehicle and water.

  According to invention of Claim 4, the space surrounding an electric coupling becomes large, and it can further protect an electric coupling from external forces, such as a stepping stone from the downward direction of a vehicle, and moisture.

1 is a block diagram showing a schematic configuration of a hybrid vehicle that is an embodiment of a vehicle on which a vehicle drive device according to the present invention can be mounted. It is a longitudinal cross-sectional view of the rear-wheel drive device of one Embodiment. FIG. 3 is an enlarged partial sectional view of an upper portion of the rear wheel drive device shown in FIG. 2. It is a perspective view which shows the state in which the vehicle drive device of FIG. 1 was mounted in the flame | frame. It is an external appearance perspective view of the rear-wheel drive device from which the electric oil pump was removed. (A) is the perspective view which looked at the lid member to which the electric oil pump was attached from the inside, (b) is the front view which looked at the lid member from the inside. It is sectional drawing of the electric oil pump along the VII-VII line of Fig.6 (a). It is a partial expanded side view of a rear-wheel drive device. It is sectional drawing of the rear-wheel drive device along the IX-IX line of FIG. It is sectional drawing of the rear-wheel drive device along the XX line of FIG. It is a partial expanded bottom view of a rear-wheel drive device.

The vehicle drive device according to the present invention uses an electric motor as a drive source for driving wheels, and is used, for example, in a vehicle having a drive system as shown in FIG. In the following description, the case where the vehicle drive device is used for rear wheel drive will be described as an example, but it may be used for front wheel drive.
A vehicle 3 shown in FIG. 1 is a hybrid vehicle having a drive device 6 (hereinafter referred to as a front wheel drive device) in which an internal combustion engine 4 and an electric motor 5 are connected in series at the front portion of the vehicle. Is transmitted to the front wheels Wf via the transmission 7, while the power of the driving device 1 (hereinafter referred to as a rear wheel driving device) provided at the rear of the vehicle separately from the front wheel driving device 6 is the rear wheel Wr. (RWr, LWr). The electric motor 5 of the front wheel drive device 6 and the first and second electric motors 2A, 2B of the rear wheel drive device 1 are connected to the battery 9 so that power supply from the battery 9 and energy regeneration to the battery 9 are possible. It has become. In FIG. 1, reference numeral 8 denotes a control device for controlling the entire vehicle.

First, the vehicle drive device of one Embodiment which concerns on this invention is demonstrated based on FIGS.
FIG. 2 is a longitudinal sectional view of the entire rear wheel drive device 1, and FIG. 3 is an enlarged partial sectional view of the upper part of FIG. In the figure, reference numeral 11 denotes a case of the rear wheel drive device 1, and the case 11 is arranged on the left and right of the central case 11 </ b> M so as to sandwich the central case 11 </ b> M between the central case 11 </ b> M and the central case 11 </ b> M. It is comprised from the side cases 11A and 11B arrange | positioned, and the whole is formed in a substantially cylindrical shape. In the case 11, there are axles 10A and 10B for the rear wheels Wr, first and second motors 2A and 2B for driving axles as power sources, and power transmission between the rear wheels LWr and RWr and the motors 2A and 2B. The first and second planetary gear type speed reducers 12A and 12B as the first and second transmissions as power transmission mechanisms arranged on the path and decelerating the drive rotation of the electric motors 2A and 2B are on the same axis. Are arranged side by side. The axle 10A, the first electric motor 2A and the first planetary gear speed reducer 12A drive and control the left rear wheel LWr, and the axle 10B, the second electric motor 2B and the second planetary gear speed reducer 12B drive the right rear wheel RWr. Control. The axle 10A, the first electric motor 2A and the first planetary gear speed reducer 12A, and the axle 10B, the second electric motor 2B and the second planetary gear speed reducer 12B are arranged symmetrically in the vehicle width direction in the case 11. Yes. The left rear wheel LWr is positioned opposite to the first planetary gear type reduction gear 12A with respect to the first electric motor 2A, and the right rear wheel RWr is also connected to the second planetary gear type reduction gear 12B with respect to the second electric motor 2B. Located on the opposite side. The first electric motor 2A and the first planetary gear type speed reducer 12A are arranged in this order from the outer side in the vehicle width direction, and the second electric motor 2B and the second planetary gear type speed reducer 12B are arranged from the outer side in the vehicle width direction. By arrange | positioning in this order, 1st and 2nd planetary gear type reduction gears 12A and 12B are arrange | positioned between 1st and 2nd electric motor 2A, 2B.

  The side cases 11A and 11B are respectively provided with partition walls 18A and 18B extending radially inward on the central case 11M side. Between the side cases 11A and 11B and the partition walls 18A and 18B, first and first partitions are provided. Two electric motors 2A and 2B are arranged. Further, first and second planetary gear speed reducers 12A and 12B are arranged in a space surrounded by the central case 11M and the partition walls 18A and 18B. As shown in FIG. 2, in this embodiment, the left side case 11A and the center case 11M constitute a first case 11L that houses the first electric motor 2A and the first planetary gear type speed reducer 12A. The right side case 11B and the center case 11M constitute a second case 11R that houses the second electric motor 2B and the second planetary gear type speed reducer 12B. The first case 11L includes a left reservoir RL that stores oil as a liquid fluid used for lubrication and / or cooling of at least one of the first electric motor 2A and the first planetary gear speed reducer 12A. The second case 11R includes a right reservoir RR that stores oil used for lubrication and / or cooling of at least one of the second electric motor 2B and the second planetary gear type speed reducer 12B. As shown in FIG. 4, the case 11 is supported by a subframe 13 that is a skeleton member of a vehicle by mount members 13 a and 13 b that are a pair of support devices, and the vehicle floor panel (see FIG. (Not shown). Moreover, the rear-wheel drive device 1 fixes the mount members 13a and 13b to the boss | hub part 11a (refer FIG. 4) projected forward from the front side surface 11f of case 11 (side case 11A, 11B). It is supported by the vehicle 3. Moreover, the arrow in FIGS. 2-11 has shown the positional relationship in the state in which the rear-wheel drive device 1 was mounted in the vehicle.

  The rear wheel drive device 1 is provided with a breather device 40 that communicates the inside and the outside of the case 11 so that the air inside is not exposed to the outside through the breather chamber 41 so that the air inside does not become excessively high temperature and pressure. Configured to escape. The breather chamber 41 is disposed at the upper part in the vertical direction of the case 11, and includes an outer wall of the central case 11M, a first cylindrical wall 43 extending substantially horizontally in the central case 11M on the left side case 11A side, and a right side case. A second cylindrical wall 44 extending substantially horizontally on the 11B side, a left and right dividing wall 45 connecting the inner ends of the first and second cylindrical walls 43, 44, and a left side case 11A of the first cylindrical wall 43. A space formed by a baffle plate 47A attached so as to abut on the side tip, and a baffle plate 47B attached so as to abut on the right side case 11B side tip of the second cylindrical wall 44. The

  The first and second cylindrical walls 43 and 44 and the left and right dividing walls 45 forming the lower surface of the breather chamber 41 are such that the first cylindrical wall 43 is located radially inward from the second cylindrical wall 44 and the left and right dividing walls 45 are The third cylindrical wall 44 extends from the inner end portion of the second cylindrical wall 44 to the inner end portion of the first cylindrical wall 43 while being bent while being reduced in diameter, and further extends radially inward to extend substantially horizontally. The cylindrical wall 46 is reached. The third cylindrical wall 46 is located inside and substantially in the center from both outer ends of the first cylindrical wall 43 and the second cylindrical wall 44.

  In the central case 11M, baffle plates 47A, 47B are planetary gear type in a space between the first cylindrical wall 43 and the outer wall of the central case 11M or a space between the second cylindrical wall 44 and the outer wall of the central case 11M. It is fixed so as to be separated from the speed reducer 12A or the planetary gear type speed reducer 12B.

  In addition, an external communication path 49 that connects the breather chamber 41 and the outside is connected to the central case 11M on the upper surface in the vertical direction of the breather chamber 41. The breather chamber side end portion 49a of the external communication passage 49 is arranged so as to be directed downward in the vertical direction. Accordingly, the oil is prevented from being discharged to the outside through the external communication passage 49.

  In the first and second electric motors 2A and 2B, stators 14A and 14B are fixed to side cases 11A and 11B, respectively, and annular rotors 15A and 15B are rotatably arranged on the inner peripheral sides of the stators 14A and 14B. Yes. Cylindrical shafts 16A and 16B surrounding the outer periphery of the axles 10A and 10B are coupled to the inner peripheral portions of the rotors 15A and 15B, and the cylindrical shafts 16A and 16B can be relatively rotated coaxially with the axles 10A and 10B. The side cases 11A and 11B are supported by end walls 17A and 17B and partition walls 18A and 18B via bearings 19A and 19B. Further, the rotation position information of the rotors 15A and 15B is fed back to the control controllers (not shown) of the electric motors 2A and 2B on the end walls 17A and 17B on the outer periphery on one end side of the cylindrical shafts 16A and 16B. Resolvers 20A and 20B are provided. The first and second electric motors 2A and 2B including the stators 14A and 14B and the rotors 15A and 15B have the same diameter, and the rotation axes of the first and second electric motors 2A and 2B are arranged on the same line x (hereinafter referred to as the following). , X is attached as the rotation axis x), and the first and second electric motors 2A and 2B are arranged in mirror symmetry with each other. The axle 10A and the cylindrical shaft 16A pass through the first electric motor 2A and extend from both ends of the first electric motor 2A. The axle 10B and the cylindrical shaft 16B also penetrate the second electric motor 2B. , Extending from both ends of the second electric motor 2B.

  Further, the first planetary gear type speed reducer 12A disposed on the power transmission path between the left rear wheel LWr and the first motor 2A, and the power transmission path between the right rear wheel RWr and the second motor 2B. The second planetary gear speed reducer 12B includes sun gears 21A and 21B, a plurality of planetary gears 22A and 22B meshed with the sun gears 21A and 21B, planetary carriers 23A and 23B that support the planetary gears 22A and 22B, and planetary gears. Ring gears 24A and 24B meshed with the outer peripheral sides of 22A and 22B, the driving forces of the electric motors 2A and 2B are input from the sun gears 21A and 21B, and the reduced driving forces are transmitted through the planetary carriers 23A and 23B to the axles 10A, 10B is output.

  The sun gears 21A and 21B are formed integrally with the cylindrical shafts 16A and 16B. The planetary gears 22A and 22B are double pinions having first pinions 26A and 26B having large diameters directly meshed with the sun gears 21A and 21B, and second pinions 27A and 27B having smaller diameters than the first pinions 26A and 26B. The first pinions 26A and 26B and the second pinions 27A and 27B are integrally formed in a state of being coaxial and offset in the axial direction. The planetary gears 22A and 22B are supported by the pinion shafts 32A and 32B of the planetary carriers 23A and 23B via needle bearings 31A and 31B, and the planetary carriers 23A and 23B have an axially inner end extending radially inward to the axle 10A. 10B and is supported by the partition walls 18A and 18B via bearings 33A and 33B.

  The ring gears 24A and 24B have gear portions 28A and 28B that are meshed with the second pinions 27A and 27B whose inner peripheral surfaces are small diameters, and small diameters that are smaller than the gear portions 28A and 28B and that are opposed to each other at an intermediate position of the case 11. Parts 29A, 29B, and connecting parts 30A, 30B for connecting the axially inner ends of the gear parts 28A, 28B and the axially outer ends of the small diameter parts 29A, 29B in the radial direction.

  The gear portions 28A and 28B face each other in the axial direction with a third cylindrical wall 46 formed at the inner diameter side end portion of the left and right dividing wall 45 of the central case 11M. The outer diameter surfaces of the small diameter portions 29A and 29B are spline-fitted to an inner race 51 of a one-way clutch 50, which will be described later, and the ring gears 24A and 24B are connected to each other so as to rotate integrally with the inner race 51 of the one-way clutch 50. Configured.

  On the planetary gear type speed reducer 12B side, between the second cylindrical wall 44 of the central case 11M constituting the case 11 and the gear portion 28B of the ring gear 24B, the hydraulic pressure is connected to the ring gear 24B and constitutes the braking means. The brake 60 is arranged so as to overlap the first pinion 26B in the radial direction and overlap the second pinion 27B in the axial direction. The hydraulic brake 60 includes a plurality of fixed plates 35 that are spline-fitted to the inner peripheral surface of the second cylindrical wall 44 and a plurality of rotary plates 36 that are spline-fitted to the outer peripheral surface of the gear portion 28B of the ring gear 24B. The plates 35 and 36 are arranged alternately in the directions, and are fastened and released by an annular piston 37. The piston 37 is accommodated in an annular cylinder chamber formed between the left and right dividing walls 45 of the central case 11M and the third cylindrical wall 46, and is provided on the outer peripheral surface of the third cylindrical wall 46. By the elastic member 39 supported by the receiving seat 38, the fixed plate 35 and the rotating plate 36 are always urged in the releasing direction.

  More specifically, the working chamber S into which oil is directly introduced is defined between the left and right dividing walls 45 and the piston 37, and when the pressure of the oil introduced into the working chamber S exceeds the urging force of the elastic member 39, The piston 37 moves forward (to the right), and the fixed plate 35 and the rotating plate 36 are pressed against each other and fastened. When the urging force of the elastic member 39 exceeds the pressure of the oil introduced into the working chamber S, the piston 37 moves backward (leftward movement), and the fixed plate 35 and the rotating plate 36 are separated and released. . The hydraulic brake 60 is connected to an electric oil pump 70 (see FIG. 4) as a liquid fluid supply device.

  In the case of this hydraulic brake 60, the fixed plate 35 is supported by the second cylindrical wall 44 extending from the left and right dividing walls 45 of the central case 11M constituting the case 11, while the rotating plate 36 is supported by the gear portion 28B of the ring gear 24B. Therefore, when the plates 35 and 36 are pressed by the piston 37, a braking force is applied to the ring gear 24B by the frictional engagement between the plates 35 and 36, and is fixed. When the fastening by the piston 37 is released from this state, the ring gear 24B is allowed to rotate freely. As described above, since the ring gears 24A and 24B are connected to each other, the braking force is also applied to the ring gear 24A when the hydraulic brake 60 is fastened, and the ring gear 24A is fixed when the hydraulic brake 60 is released. Free rotation is allowed.

  Also, a space is secured between the coupling portions 30A and 30B of the ring gears 24A and 24B facing each other in the axial direction, and only power in one direction is transmitted to the ring gears 24A and 24B in the space to transmit power in the other direction. A one-way clutch 50 is arranged to be shut off. The one-way clutch 50 has a large number of sprags 53 interposed between an inner race 51 and an outer race 52. The inner race 51 is connected to the small diameter portions 29A, 29B of the ring gears 24A, 24B by spline fitting. It is configured to rotate integrally. The outer race 52 is positioned by the third cylindrical wall 46 and is prevented from rotating.

  The one-way clutch 50 is configured to engage and lock the rotation of the ring gears 24A and 24B when the vehicle 3 moves forward with the power of the electric motors 2A and 2B. More specifically, the one-way clutch 50 is engaged when rotational power in the forward direction on the motors 2A, 2B side (rotation direction when the vehicle 3 is advanced) is input to the wheel Wr side. When the rotational power in the reverse direction on the electric motors 2A and 2B is input to the wheels Wr, the non-engagement state is established, and when the rotational power in the forward direction on the wheels Wr is input to the electric motors 2A and 2B, it is not engaged. The engaged state is established when the rotating power in the reverse direction on the wheel Wr side is input to the electric motors 2A, 2B while being engaged.

Thus, in the rear wheel drive device 1 of the present embodiment, the one-way clutch 50 and the hydraulic brake 60 are provided in parallel on the power transmission path between the electric motors 2A, 2B and the wheels Wr. It should be noted that the hydraulic brake 60 is released, weakly engaged, or engaged by the pressure of oil supplied from the oil pump 70 according to the running state of the vehicle and the engaged / disengaged state of the one-way clutch 50. Be controlled. For example, when the vehicle 3 moves forward by powering drive of the electric motors 2A and 2B (at low vehicle speed and medium vehicle speed), the one-way clutch 50 is engaged, so that power can be transmitted but the hydraulic brake 60 is weakly engaged. Therefore, even when the input of forward rotational power from the motors 2A and 2B side temporarily decreases and the one-way clutch 50 is disengaged, the motors 2A and 2B Inability to transmit power to the wheel Wr side is suppressed. Further, when the vehicle 3 moves forward by power driving of the internal combustion engine 4 and / or the electric motor 5 (at the time of high vehicle speed), the one-way clutch 50 is disengaged and the hydraulic brake is controlled to be in a released state, so that the electric motor Over-rotation of 2A and 2B is prevented. On the other hand, when the vehicle 3 moves backward or regenerates, the one-way clutch 50 is disengaged, so that the hydraulic brake 60 is controlled to be in the engaged state, so that the rotational power in the reverse direction from the electric motors 2A and 2B is changed to the wheels Wr Or forward rotational power on the wheel Wr side is input to the electric motors 2A and 2B.

  As shown in FIG. 5, the outer peripheral surfaces of the first and second cylindrical walls 43, 44 and the left and right dividing walls 45 of the central case 11 </ b> M are exposed to the outside at portions other than forming the breather chamber 41. On the outer peripheral surfaces of the first and second cylindrical walls 43 and 44 and the left and right dividing walls 45, a pair of projecting portions 101 and 102 projecting radially from both axial end portions are formed.

  Then, around the first and second cylindrical walls 43, 44 and the left and right dividing walls 45, a substantially square shape is formed by a pair of projecting portions 101, 102, a bottom wall 103, and an upper wall 104 obliquely forward and downward. A strainer accommodating chamber 105 is formed which is defined in a cylindrical shape and accommodates a strainer 71 described later.

  The pair of overhanging portions 101 and 102 forming the strainer accommodating chamber 105 includes through holes 107a and 107b (see FIG. 5) communicating the left reservoir RL and the strainer accommodating chamber 105, and the right reservoir RR and the strainer accommodating chamber. A through hole 107 c (not shown) that communicates with 105 is formed. Thereby, the strainer accommodation chamber 105 arranged between the left reservoir RL and the right reservoir RR communicates the left reservoir RL and the right reservoir RR.

  The front opening 105a of the strainer accommodating chamber 105 is closed by fastening and fixing a lid member 72 to which the electric oil pump 70 is attached with a plurality of bolts 106, and the inner wall surface of the lid member 72 is the strainer accommodating chamber. The outer wall surface 72 b of the lid member 72 constitutes the side surface of the case 11.

As shown in FIG. 6, the strainer 71 has a discharge port 71 a inserted into the lid member 72, and is tightened together with a bolt 69 that fastens the oil passage forming cover 96 to the lid member 72. It is detachably fixed. The strainer 71 removes foreign matter from the oil sucked from a suction port (not shown) provided on the lower surface thereof, and the oil from which the foreign matter has been removed is sent to the electric oil pump 70.
The strainer 71 that constitutes the oil suction path 94 together with the electric oil pump 70 and the lid member 72 extends to the case side from the case fixing portion 72d of the lid member 72. The strainer 71 has an inlet for the strainer 71. In the attached state, which is fastened and fixed to the front opening 105 a of the storage chamber 105, the storage chamber 105 is located in the storage portion.

  As shown in FIGS. 6 and 7, the electric oil pump 70 is a so-called trochoid pump, which is driven by another electric motor 90 composed of a position sensorless / brushless DC motor and performs PID control based on a target rotational speed and the like. It is controlled. Then, while adjusting the discharge amount by rotating an unillustrated inner rotor or outer rotor provided in the suction portion 93, the oil flowed from the strainer 71 into the oil suction passage 94 provided in the electric oil pump 70 and the lid member 72. Oil is discharged to an oil discharge passage 95 as an intermediate fluid passage provided in the electric oil pump 70 and the lid member 72.

  Further, as shown in FIGS. 7, 9 and 10, the lid member 72 has an extending part 72a extending from the case 11 in a substantially horizontal direction and forming an oil discharge passage 95. The extending part 72a A base portion 70b of an electric oil pump 70 that forms an oil discharge path 95 together with the extending portion 72a is connected to the end portion 72a1. The electric oil pump 70 is attached to the lid member 72 so as to be positioned in front of the lid member 72 when the lid member 72 is fixed to the case 11, and is substantially perpendicular to the extending portion 72 a of the lid member 72. It arrange | positions so that it may extend upwards. Inside the lid member 72, an oil passage forming cover 96 that defines a part of the oil passage 99 together with the lid member 72 is fixed by bolts 69. Between the lid member 72 and the oil passage forming cover 96, a low pressure oil passage switching valve 73, a brake oil passage switching valve 74, and a relief valve 84, which will be described later, are arranged in order from the bottom. Further, as shown in FIGS. 8 to 11, solenoid valves 85 and 86 are attached to the side of the lid member 72 opposite to the oil passage forming cover 96. Shut off.

  The oil passage forming cover 96 includes a working chamber port 108a of a brake oil passage 77, which will be described later, formed in the outer peripheral surface of the central case 11M in the strainer accommodating chamber 105, and first and second cold and humid flows described later. Two outlet pipes 97a and 97b connected to the cooling / lubricating ports 108b of the paths 130A and 130B, respectively, are attached.

  That is, as described above, the outlet pipes 97a and 97b are connected to the working chamber port 108a in a state where the lid member 72 to which the electric oil pump 70 is attached is attached to the front opening 105a of the strainer accommodating chamber 105. It is connected to the cooling / lubricating port 108b.

  Couplers 87 and 88 are attached to the solenoid valves 85 and 86, respectively. The solenoid valves 85 and 86 are connected to the electric wires 89a and 89b through the couplers 87 and 88, respectively. Moreover, these electric wires 89a and 89b are integrated in the wiring part 83, and are wired to a control apparatus or a power supply.

Here, as shown in FIGS. 8 to 11, at least a part of the couplers 87 and 88 includes an outer wall surface 72 b of the lid member 72, an upper surface 72 a 2 of the extension portion 72 a of the lid member 72, and a base portion 70 b of the electric oil pump 70. , And the space T surrounded on three sides by the inner side surface 70a of the electric oil pump 70 facing the outer wall surface 72b of the lid member 72. In particular, in the present embodiment, as shown in FIG. 11, the couplers 87 and 88 are entirely surrounded by the upper surface 72 a 2 of the extending portion 72 a of the lid member 72 and the base portion 70 b of the electric oil pump 70. Therefore, the couplers 87 and 88 prevent the direct hit of the stepping stone from the front of the vehicle and the direct hit of the water flow by the car wash from directly below by the lid member 72 and the electric oil pump 70, and without setting a separate protective cover or the like. Can be protected.
Further, as shown in FIG. 8, at least a part of the couplers 87 and 88 is surrounded on both the left and right sides by a pair of mount members 13a and 13b. Further, the couplers 87 and 88 are surrounded by the subframe 13 so that the couplers 87 and 88 can be protected from external force and water from above the vehicle.

As shown in FIGS. 9 and 10, the inner side surface 70 a of the electric oil pump 70 includes a first side surface 70 a 1 near the outer wall surface 72 b of the lid member 72, a lower side than the first side surface 70 a 1, and a first side surface 70 a 1. And a second side surface 70a2 spaced from the outer wall surface 72b, and a recess 70c is formed with the base portion 70b. The couplers 87 and 88 are disposed at positions facing the second side surface 70a2 in the front-rear direction of the vehicle, and are partially accommodated in the recess 70c.
Furthermore, the couplers 87 and 88 are arranged so as to partially overlap each other when viewed from the direction of the rotation axis x, and the plurality of couplers 87 and 88 are efficiently arranged in the constrained space T.

  The case 11 is formed with a brake oil passage (not shown) that communicates from the working chamber port 108 a to the working chamber S of the hydraulic brake 60, and is supplied with oil discharged from the electric oil pump 70. Further, the case 11 includes a front vertical oil passage 109 extending in the vertical direction from the cooling / lubricating port 108b in the front portion of the central case 11M, a left case oil passage 110A branched from the front vertical oil passage 109, and a right case oil passage. 110B. In the left case oil passage 110A, the oil passing through the oil passage 110A cools the cooled portion A1 of the first electric motor 2A (for example, the coil of the stator 14A of the first electric motor 2A). The portion to be lubricated A2 (for example, the bearing 19A of the first electric motor 2A) is formed to be lubricated, and is formed to communicate with the left axle oil passage 111A provided on the axle 10A. The oil passing through the left axle oil passage 111A is lubricated by the lubricated portion A3 of the first planetary gear speed reducer 12A (for example, the needle bearing 31A of the first planetary gear speed reducer 12A and the gears 21A, 22A, 23A, 24A meshing part etc.) is lubricated.

  Also, in the right case oil passage 110B, the oil that has passed through the oil passage 110B cools the cooled portion B1 of the second electric motor 2B (for example, the coil of the stator 14B of the second electric motor 2B), and the second electric motor It is formed so as to lubricate the lubricated portion B2 of 2B (for example, the bearing 19B of the second electric motor 2B) and communicate with the right axle oil passage 111B provided on the axle 10B. The oil passing through the right axle oil passage 111B is lubricated by the lubricated portion B3 of the second planetary gear type reduction gear 12B (for example, the needle bearing 31B of the second planetary gear type reduction gear 12B and the gears 21B, 22B, 24B). Lubricate the meshing part).

  Therefore, the front vertical oil passage 109, the left case oil passage 110A, and the left axle oil passage 111A formed in the case 11 are the cooled portion A1 and the lubricated portion A2 of the first electric motor 2A, and the first planetary gear type reduction gear. The first cooling fluid passage 130A for cooling the lubricated portion A3 of the machine 12A is configured, and the front vertical oil passage 109, the right case oil passage 110B, and the right axle oil passage 111B formed in the case 11 are the second electric motor. A second cooling channel 130B for cooling the cooled portion B1 and the lubricated portion B2 of 2B and the lubricated portion B3 of the second planetary gear speed reducer 12B is configured.

As described above, according to the rear wheel drive device 1 of the present embodiment, the case 11 extends substantially horizontally from the side surface of the case 11, that is, from the outer wall surface 72 b of the lid member 72. The first and second cooling flow passages 130A, 130B and the electric oil pump 70 are connected to each other, and an oil discharge passage 95 is formed. The end 72a1 of the extension 72a of the lid member 72 is disposed so as to extend substantially upward in the vertical direction from the extension 72a.
Then, in a space T surrounded on three sides by the outer wall surface 72b of the lid member 72, the upper surface 72a2 of the extending portion 72a of the lid member 72, and the inner surface 70a of the electric oil pump 70 facing the outer wall surface 72b of the lid member 72. Since the couplers 87 and 88 are disposed on the electric wires 89a and 89b for supplying power to the solenoid valves 85 and 86, the couplers 87 and 88 can be used as stepping stones from the front, rear, and lower sides of the vehicle. It can be protected from external force and moisture.

  A pair of mount members 13a and 13b for supporting the vehicle drive device 1 on the subframe 13 are attached to both sides of the outer wall surface 72b of the lid member 72 in the axial direction. Since both sides are surrounded by the mounting members 13a and 13b, the couplers 87 and 88 can be further protected from external forces such as stepping stones from the left and right sides of the vehicle and water.

  Further, since the vehicle drive device 1 is supported by the subframe 13 and the couplers 87 and 88 are surrounded by the subframe 13, the couplers 87 and 88 are further separated from the external force such as a stepping stone from the upper side of the vehicle or water. Can be protected.

  Further, the electric oil pump 70 is connected to the end portion 72a1 of the extending portion 72a of the lid member 72 and has a base portion 70b extending in a substantially horizontal direction and having an oil discharge path 95 formed therein. The surrounding space becomes larger, and the couplers 87 and 88 can be further protected from external force such as stepping stones from the lower side of the vehicle and water.

  Also, the inner side surface 70a of the electric oil pump 70 is a first side surface 70a1 near the outer wall surface 72b of the lid member 72, and a second side surface that is below the first side surface 70a1 and is farther from the outer wall surface 72b than the first side surface 70a1. 70a2 and the couplers 87 and 88 are disposed at positions facing the second side surface 70a2 in the front-rear direction of the vehicle. Therefore, the electric oil pump 70 is also protected and restricted from external force and moisture from above. The couplers 87 and 88 are efficiently arranged using the space T effectively.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.

  In the present embodiment, the side surface of the housing of the present invention that constitutes the space is configured by the outer wall surface 72b of the lid member 72. However, the side surface of the housing of the present invention is not limited to this, and the case 11 may be formed. Further, the flow path forming portion of the present invention may also be formed by the case 11 and extend from the side surface of the case 11.

  In the present embodiment, the couplers 87 and 88 are provided above the upper surfaces 72a2 and 70b1 of both the extending portion 72a of the lid member 72 and the base portion 70b of the electric oil pump 70. It may be provided only on the upper surface, that is, above the upper surface 72a2 of the extending portion 72a of the lid member 72.

  In addition, in the present embodiment, the couplers 87 and 88 that are interposed on the electric wires that supply power to the solenoid valves 85 and 86 that are electric drive parts have been described as the electric coupling of the present invention, but the present invention is not limited thereto. It may be interposed on an electric wire for supplying an electric signal or electric power to other electric drive parts, or may be interposed on an electric wire for supplying an electric signal or electric power to the electric oil pump 70. It may be a thing.

Further, the front wheel drive device 6 may use the electric motor 5 as a sole drive source without using the internal combustion engine 4.
Further, as the power source, another driving force generator such as an internal combustion engine may be used instead of the electric motors 2A and 2B.

  In the present embodiment, the left case 11A and the central case 11M constitute a first case 11L, and the right case 11B and the central case 11M constitute a second case 11R. However, as long as the first case 11L of the present invention accommodates the first electric motor 2A and the first planetary gear type speed reducer 12A and has the left reservoir RL, the second case 11R is the second electric motor. The structure is not limited to this as long as it accommodates 2B and the second planetary gear type speed reducer 12B and has the right reservoir RR.

  Furthermore, in the embodiment as shown in FIGS. 2 to 11, the first transmission is on the power transmission path between the left wheel and the first electric motor 2A, and the power transmission path between the right wheel and the second electric motor 2B is on. Although the second transmission is configured to be respectively disposed, the present invention may be configured to include the first and second electric motors 2A and 2B without including the first and second transmissions.

  In the present invention, oil is used as the liquid fluid used for cooling and lubrication, but other liquids may be used.

1 Rear wheel drive system (vehicle drive system)
2A 1st electric motor (power source)
2B Second electric motor (power source)
11 Case (housing)
11L 1st case 11R 2nd case 12A 1st planetary gear type reduction gear (power transmission mechanism)
12B Second planetary gear type speed reducer (power transmission mechanism)
70 Electric oil pump (liquid fluid supply device)
70a Inner side surface (side surface of liquid fluid supply device)
71 Strainer 72 Lid member 72a Extension part (flow path forming part)
72a1 end 72a2 upper surface 72b outer wall surface (side surface of housing)
87, 88 coupler (electrical coupling)
89a, 89b Electric wire 95 Oil discharge path (intermediate flow path forming part)
105 Strainer storage chamber 130A 1st cooling flow path 130B 2nd cooling flow path A1, B1 Cooled part A2, B2 Lubricated part A3, B3 Lubricated part LWr Left rear wheel (wheel)
RWr Right rear wheel (wheel)

Claims (4)

A housing that houses at least one of a power source of a vehicle, a power transmission mechanism disposed on a power transmission path between the wheels of the vehicle and the power source, and
A liquid fluid supply device that supplies a liquid fluid to a cooled portion that is at least one of a cooled portion and a lubricated portion of the power source, and a cooled portion and a lubricated portion of the power transmission mechanism;
A vehicle drive device comprising:
The casing extends in a substantially horizontal direction from a side surface of the casing, and a flow is formed in which an intermediate fluid flow path that connects the liquid fluid flow path formed in the casing and the liquid fluid supply device is formed. Having a path forming section,
The liquid fluid supply device is disposed at an extending end of the flow path forming portion so as to extend substantially vertically above the flow path forming portion,
In the space surrounded by the side surface of the housing, the upper surface of the flow path forming unit, and the side surface of the liquid fluid supply device facing the side surface of the housing, an electric drive component installed in the housing Or an electric coupling interposed on an electric wire for supplying an electric signal or electric power to the liquid fluid supply device ,
The side surface of the liquid fluid supply device includes a first side surface near the side surface of the housing, and a second side surface that is below the first side surface and is further away from the side surface of the housing than the first side surface. Prepared,
The vehicle drive device according to claim 1, wherein the electrical coupling is disposed at a position facing the second side surface in the front-rear direction of the vehicle. A pair of support devices for supporting the vehicle drive device on a skeleton member of the vehicle is attached to the side surface of the housing.
The vehicle drive device according to claim 1, wherein the electric coupling is surrounded on both sides by the pair of support devices. The vehicle drive device is supported by a skeleton member of the vehicle,
The vehicle drive device according to claim 1, wherein the electric coupling is surrounded by the skeleton member.   The liquid fluid supply device is connected to an extending end of the flow path forming portion, extends in a substantially horizontal direction, and has a base portion on which the intermediate fluid flow path is formed. The vehicle drive device according to any one of the above.

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