JP6232268B2 - 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 preventing parts outside a housing from being corroded by accumulated water.

  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 and placed outside the case.

JP2013-13195A

  By the way, in the vehicle drive device described in Patent Document 1, there is a possibility that water on the case may stay on the upper surface of the lid member, and when the water accumulates on the lid member, a solenoid valve that is a peripheral component of the lid member And bolts could corrode.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a vehicle drive device that can suppress water that has flowed over a housing from flowing onto the upper surface of the extension portion. It is in.

In order to achieve the above object, the invention described in claim 1
A power transmission path between an electric motor (for example, electric motors 2A and 2B in an embodiment described later) mounted on the vehicle, a wheel of the vehicle (for example, a left rear wheel LWr and a right rear wheel RWr in an embodiment described later), and the electric motor. A housing (for example, a case of an embodiment described later) that houses at least one of a power transmission mechanism (for example, the first and second planetary gear speed reducers 12A, 12B of the embodiment described later) disposed on the upper side. 11) and
An accessory device (for example, an electric oil pump 70 according to an embodiment described later) fixed to the outer surface of the housing;
A vehicle drive device (for example, a rear wheel drive device 1 according to an embodiment described later),
Wherein the housing, the extending portion extending in horizontal direction (e.g., extension portion 72a of the lid member 72 of the embodiment) is provided,
The accessory is fixed to an extension end of the extension part (for example, an end part 72a1 of an extension part 72a in an embodiment described later) so as to extend substantially vertically above the extension part. And
The extension portion is recessed on the upper surface in the vertical direction of the extension portion (for example, the upper surface 72a2 of the extension portion 72a of the embodiment described later), and the side surface of the extension portion (for example, the left side of the embodiment described later) It has a groove part (for example, groove part 91 of below-mentioned embodiment) extended to the surface 72a3).

Moreover, in addition to the structure of Claim 1, the invention of Claim 2 is
It further has another accessory device (for example, a solenoid valve 86 in an embodiment described later) different from the accessory device,
The other accessory device is fixed to the housing so that at least a part thereof is located in the groove.

In addition to the configuration described in claim 1 or 2, the invention described in claim 3
The groove portion is only one of the side surface (for example, the left side surface 72a3 in the embodiment described later) and the other side surface (for example, the right side surface 72a4 in the embodiment described later). It is characterized by extending up to.

Moreover, in addition to the structure of Claim 3, the invention of Claim 4 adds to the structure of Claim 3,
The accessory device is fixed to the extension part by a fastening member (for example, a fastening bolt 120 in an embodiment described later) arranged along the extension direction of the extension part,
The groove portion is formed on the upper surface in the vertical direction along a direction orthogonal to the extending direction of the extending portion.

Moreover, in addition to the structure in any one of Claims 1-4, the invention of Claim 5 is
The extension part is formed as a separate body so as to be detachable from the housing.

Moreover, in addition to the structure in any one of Claims 1-5, the invention of Claim 6 is
The accessory device is a liquid fluid supply device,
The extension portion is an intermediate fluid flow that communicates a flow path formed in the housing (for example, first and second cooling flow paths 130A and 130B in the embodiments described later) and the liquid fluid supply device. It has a path (for example, an oil discharge path 95 in an embodiment described later).

  According to the first aspect of the present invention, the attachment device is fixed to the housing through the extending portion, whereby the rigidity of the pedestal portion for fixing the attachment device can be improved. It is possible to suppress the water flowing down and staying on the upper surface of the extending portion.

  According to the second aspect of the present invention, the other accessory device and the extending portion can be arranged closer to each other, and the vehicle drive device can be made compact in the vertical direction.

  According to the invention of claim 3, since the water in the groove portion can be discharged only by one side surface, it is not necessary to perform the groove processing to an unnecessary portion on the upper surface in the vertical direction.

  According to invention of Claim 4, since the surface in which the fastening member which fastens an attachment member is provided differs from one side surface which discharges the water in a groove part, it suppresses that a fastening member corrodes by the waste_water | drain from a groove part. be able to.

  According to the fifth aspect of the present invention, it is possible to easily check and maintain the condition of the groove.

  According to the sixth aspect of the present invention, the flow path length between the liquid fluid supply device and the housing can be increased, and the pulsation of the liquid fluid supply device can be reduced. Further, the surface area of the intermediate fluid flow path is increased by the extending portion, and the heat dissipation effect of the liquid fluid flowing inside is obtained.

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 the partial expansion perspective view which looked at the rear-wheel drive device from the diagonally left front. It is the elements on larger scale which looked at the rear-wheel drive device from which the electric oil pump was removed from diagonally left front. It is sectional drawing of the rear-wheel drive device along the XI-XI line of FIG.

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 vehicle skeleton member by mount members 13 a and 13 b that are a pair of support devices, and a vehicle floor panel (not shown) is interposed through the subframe 13. Z)). 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 same”). , X is attached as the rotation axis X.) Also, 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 detachably 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 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. When the lid member 72 is fixed to the case 11, the electric oil pump 70 is attached to the lid member 72 with a fastening bolt 120 so as to be positioned in front of the lid member 72, and from the extending portion 72 a of the lid member 72. Is also arranged to extend substantially upward in the vertical direction. 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. In FIG. 6, reference numeral 92 denotes an oil sensor that detects oil pressure, temperature, and the like in the oil passage 99.

  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. 9 to 11, a groove 91 extending from the mounting hole opening 72a5 of the solenoid valve 86 to the left side surface 72a3 of the extending portion 72a extends on the vertical upper surface 72a2 of the extending portion 72a. It is recessed along the direction (left-right direction) orthogonal to the extending direction of the protrusion part 72a. As a result, the water that is caught on the case 11 and flows between the electric oil pump 70 and the solenoid valves 85 and 86 passes through the groove portion 91 as shown by the arrow A in FIG. 9, and is on the left side of the extending portion 72a. Since it flows down from the surface 72a3, it can suppress that water retains on the upper surface 72a2 of the extension part 72a. Further, since no bolts or the like are provided on the left side surface 72a3, the bolts and the like are not corroded by water flowing down the left side surface 72a3.

  Furthermore, since the solenoid valve 86 is fixed to the lid member 72 so that a part of the solenoid valve 86 is located in the groove portion 91, the solenoid valve 86 and the extending portion 72a can be arranged closer to each other. In particular, as shown in FIG. 10, the groove portion 91 is formed to extend only from the mounting hole opening 72a5 of the solenoid valve 86 formed in the lid member 72 to the left side surface 72a3, and on the right side surface 72a4 (see FIG. 5) side. Is not formed. That is, on the right side of the mounting hole opening 72a5, the outer wall surface 72b of the lid member 72 is formed continuously with the upper surface 72a2 in the vertical direction, and the rigidity of the lid member 72 is ensured.

  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 has the extending portion 72a of the lid member 72 extending from the case 11 in the substantially horizontal direction, and the electric oil pump 70 is The end portion 72a1 of the extension portion 72a is fixed so as to extend substantially upward in the vertical direction from the extension portion 72a. The extending portion 72a has a groove 91 that is recessed in the vertical upper surface 72a2 of the extending portion 72a and extends to the side surface of the extending portion 72a. Therefore, the electric oil pump 70 is fixed to the case 11 via the extension portion 72a, so that the rigidity of the pedestal portion for fixing the electric oil pump 70 can be improved. It is possible to suppress the spilled water from staying on the upper surface 72a2 of the extending portion 72a.

  In addition, since the solenoid valve 86 is fixed to the case 11 so that at least a part of the solenoid valve 86 is located in the groove portion 91, the solenoid valve 86 and the extending portion 72a can be arranged closer to each other. The drive device 1 can be made compact in the vertical direction.

  Furthermore, since the groove portion 91 extends to the side surface only at the left side surface 72a3 of the extension portion 72a, the water in the groove portion 91 can be discharged only by the left side surface 72a3, and the upper surface 72a2 connected to the right side surface 72a4 is unnecessary. There is no need to groove the part.

  The electric oil pump 70 is fixed to the extending portion 72a by fastening bolts 120 arranged along the extending direction of the extending portion 72a, and the groove portion 91 is orthogonal to the extending direction of the extending portion 72a. It is formed on the vertical upper surface 72a2 along the direction. Thereby, since the head of the fastening bolt 120 is provided on the front surface and is different from the left side surface 72a3 that discharges the water in the groove portion 91, the fastening bolt 120 can be prevented from being corroded by drainage from the groove portion 91.

  Moreover, since the extension part 72a is comprised by the cover member 72 formed separately so that attachment or detachment with respect to the case 11, the situation confirmation and maintenance of the groove part 91 can be performed easily.

  Furthermore, since the extending portion 72a has an oil discharge passage 95 that communicates the first and second cooling flow passages 130A and 130B formed in the case 11 and the electric oil pump 70, the electric oil pump 70 The length of the oil discharge path 95 between the cases 11 can be increased, and the pulsation of the electric oil pump 70 can be reduced. Further, the groove portion 91 increases the surface area of the extending portion 72 a, and the heat dissipation effect of the oil flowing through the oil discharge path 95 is obtained.

In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.
In the present embodiment, the electric oil pump 70 is fixed to the outer surface of the case 11, but the accessory device of the present invention is not limited to this.

  Moreover, although the extension part of this invention is comprised by the cover member 72 in this embodiment, the structure formed by the case 11 and extending from the side surface of the case 11 may be sufficient.

  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.

  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 (electric motor)
2B Second electric motor (electric motor)
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 (accessory equipment, liquid fluid supply device)
71 Strainer 72 Lid member 72a Extension part 72a1 End part 72a2 Upper surface 72a3 Left side surface (one side surface)
72a4 right side (the other side)
85, 86 Solenoid valve (other accessories)
95 Oil discharge passage (intermediate flow body passage)
105 Strainer chamber LWr Left rear wheel (wheel)
RWr Right rear wheel (wheel)

Claims (6)

A housing that houses at least one of an electric motor mounted on the vehicle and a power transmission mechanism disposed on a power transmission path between the vehicle wheel and the motor;
An accessory device fixed to the outer surface of the housing;
A vehicle drive device comprising:
Wherein the housing, the extending portion is provided extending in horizontal direction,
The accessory is fixed to the extending end of the extending part so as to extend substantially vertically above the extending part,
The vehicle drive device according to claim 1, wherein the extension part has a groove part that is recessed in a vertical upper surface of the extension part and extends to a side surface of the extension part. Further having another accessory device different from the accessory device,
2. The vehicle drive device according to claim 1, wherein the other accessory device is fixed to the housing such that at least a part of the other accessory device is located in the groove portion.   3. The vehicle drive device according to claim 1, wherein the groove portion extends to only one of the one side surface and the other side surface of the extension portion. 4. The accessory is fixed to the extension by a fastening member disposed along the extension direction of the extension,
4. The vehicle drive device according to claim 3, wherein the groove portion is formed on the upper surface in the vertical direction along a direction orthogonal to the extending direction of the extending portion.   The vehicle drive device according to any one of claims 1 to 4, wherein the extension portion is formed separately from the housing so as to be detachable. The accessory device is a liquid fluid supply device,
The said extension part has an intermediate | middle fluid flow path which connects the flow path formed in the said housing | casing, and the said liquid fluid supply apparatus, The any one of Claims 1-5 characterized by the above-mentioned. Vehicle drive device.

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