JP6163423B2 - Power equipment - Google Patents

Description

  The present invention relates to a power unit, and more particularly to a power unit including a liquid medium pumping device.

  Conventionally, in the transmission unit described in Patent Document 1, a control valve unit is provided at the lower end of the transmission unit, and the electric oil pump is provided in a recess provided in the housing so as to overlap a part of the control valve unit. Thus, a compact transmission unit is known.

JP 2001260674 A

  By the way, in the electric oil pump which is a supply source of the hydraulic pressure for controlling the transmission mechanism and lubricating, if the oil leaking from the pressure feeding part is not discharged to the case side, the oil may enter the motor part driving the pressure feeding part. was there. In the transmission unit described in Patent Document 1, the configuration inside the electric oil pump is not specifically disclosed.

  The present invention has been made in view of the above-described problems. The purpose of the present invention is to be able to lubricate the sealing member at normal times, and in the unlikely event that the sealing member is poorly sealed, the motor side is liquid. An object of the present invention is to provide a power unit capable of continuing to drive a liquid medium pumping device even when a medium enters.

In order to achieve the above object, the invention described in claim 1
A vehicle power source (for example, first and second electric motors 2A and 2B in an embodiment described later), a vehicle wheel (for example, a left rear wheel LWr and a right rear wheel RWr in an embodiment described later), and a power source A housing (for example, described later) that houses at least one of a power transmission mechanism (for example, first and second planetary gear speed reducers 12A, 12B in the embodiments described later) disposed on the power transmission path. Case 11) of the embodiment,
It is provided so as to be detachable with respect to the casing, and to-be-cooled parts of the power source (for example, cooled parts A1 and B1 in the embodiments described later) or lubricated parts (for example, lubricated parts A2 in the embodiments described later, B2), or an electric motor that supplies a liquid medium to a cooled portion that is at least one of a cooled portion or a lubricated portion (for example, a lubricated portion A3 or B3 in an embodiment described later) of the power transmission mechanism. A drive-type liquid medium pumping device (for example, an electric oil pump 70 according to an embodiment described later);
A power device (for example, a rear wheel drive device 1 according to an embodiment described later),
The liquid medium pumping device includes a pumping body (for example, a trochoid pump 86 in an embodiment described later) for pumping the liquid medium and an electric motor (for example, an electric motor 90 in an embodiment described later) for driving the pumping body. The rotating shaft of the electric motor (for example, the rotating shaft 90a of the embodiment described later) is arranged so as to be perpendicular or inclined with respect to the horizontal plane, and the pressure feeding body is arranged at a position lower in the vertical direction than the electric motor,
The liquid medium pressure feeding device is disposed in sliding contact with the outer periphery of the rotating shaft, and includes a sealing member (for example, an oil seal 98 in an embodiment described later) that partitions the pressure feeding body and the electric motor, and the sealing member. Is also disposed on the pumping body side and discharges the liquid medium leaked from the pumping body into the casing (for example, a leak recovery hole 131a, leak recovery grooves 135a and 135b, and a drainage path 140 in the embodiment described later). A longitudinal hole 141), and
The most downstream end (for example, the most downstream end 140a in the embodiment described later) that is the open end of the drainage channel on the housing side is vertically connected to the rotor of the motor (for example, the rotor in the embodiment described later). 91) and an intermediate middle point (for example, an upper and lower intermediate point C in an embodiment described later) and the sealing member.

The invention according to claim 2
Arranged on a power transmission path between a vehicle wheel (for example, a left rear wheel LWr and a right rear wheel RWr in an embodiment described later) and a power source (for example, first and second electric motors 2A, 2B in an embodiment described later). Hydraulic drive type connecting / disconnecting means (for example, a hydraulic brake 60 according to an embodiment described later) for switching the power transmission path between a disconnected state and a connected state;
A housing (for example, a case 11 and a lid member 72 in an embodiment described later) that accommodates the connection / disconnection means;
An electrically driven liquid medium pumping device (for example, described later) that is detachably attached to the casing and supplies a liquid medium to a hydraulic chamber (for example, a working chamber S in the embodiment described later) of the connection / disconnection means. Electric oil pump 70) of the embodiment;
A power device (for example, a rear wheel drive device 1 according to an embodiment described later),
The liquid medium pumping device includes a pumping body (for example, a trochoid pump 86 in an embodiment described later) for pumping the liquid medium and an electric motor (for example, an electric motor 90 in an embodiment described later) for driving the pumping body. The rotating shaft of the electric motor is arranged so as to be perpendicular or inclined with respect to a horizontal plane, and the pumping body is arranged at a lower position in the vertical direction than the electric motor,
The liquid medium pressure feeding device is disposed in sliding contact with the outer periphery of the rotating shaft, and includes a sealing member (for example, an oil seal 98 in an embodiment described later) that partitions the pressure feeding body and the electric motor, and the sealing member. Is also disposed on the pumping body side and discharges the liquid medium leaked from the pumping body into the casing (for example, a leak recovery hole 131a, leak recovery grooves 135a and 135b, and a drainage path 140 in the embodiment described later). A longitudinal hole 141), and
The most downstream end (for example, the most downstream end 140a in the embodiment described later) that is the open end of the drainage channel on the housing side is vertically connected to the rotor of the motor (for example, the rotor in the embodiment described later). 91) and an intermediate middle point (for example, an upper and lower intermediate point C in an embodiment described later) and the sealing member.

In addition to the configuration described in claim 1 or 2, the invention described in claim 3
A separate member (for example, an oil passage forming cover 96 in an embodiment described later) provided to be removable from the inner surface of the housing;
The drainage path is formed across the liquid medium pumping device, the housing, and the separate member,
The most downstream end portion is formed on a joint surface between the casing and the separate member or the separate member.

Moreover, in addition to the structure in any one of Claims 1-3, the invention of Claim 4 is
The housing includes a storage unit (for example, a strainer storage chamber 105 in an embodiment described later) that stores the liquid medium inside the housing.
A dynamic oil surface (for example, a dynamic oil surface H in an embodiment described later) of the storage unit is set to be lower than the vertical middle point in the vertical direction.

  According to the first aspect of the present invention, the sealing member can be lubricated by the leaked liquid medium in a normal state. In addition, the sealing member should be poorly sealed, and the liquid medium has entered the motor side. However, since more than half of the rotor of the electric motor is not immersed, the liquid medium pumping device can be continuously driven.

  According to the second aspect of the present invention, the sealing member can be lubricated by the leaked liquid medium in a normal state, and the sealing member should be poorly sealed, so that the liquid medium enters the motor side. However, since more than half of the rotor of the electric motor is not immersed, the liquid medium pumping device can be continuously driven.

  According to the invention of claim 3, the degree of freedom of arrangement is higher than when the most downstream end of the drainage path is formed in the housing, and the drainage path to the most downstream end can be easily formed. .

  According to the invention of claim 4, when a sealing failure of the sealing member occurs, it is possible to reliably prevent more than half of the rotor of the electric motor from being immersed.

1 is a block diagram showing a schematic configuration of a hybrid vehicle that is an embodiment of a vehicle on which a power unit 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 schematic sectional drawing of an electric oil pump. It is sectional drawing of the cover member and electric oil pump which followed the IX-IX line of FIG. It is a perspective view which shows the cover member of the state from which the electric oil pump was removed. It is sectional drawing of an electric oil pump and the side view of a rear-wheel drive device for demonstrating the case where the most downstream end part of a drainage path exists in an appropriate position. It is sectional drawing of an electric oil pump and the side view of a rear-wheel drive device for demonstrating the case where the most downstream end part of a drainage path exists above an appropriate position. It is sectional drawing of an electric oil pump and the side view of a rear-wheel drive device for demonstrating the case where the most downstream end part of a drainage path exists below an appropriate position.

The power unit according to the present invention uses an electric motor as a driving source for driving wheels, and is used in a vehicle having a driving system as shown in FIG. 1, for example. In the following description, the case where the power unit is used for driving rear wheels will be described as an example, but it may be used for driving front wheels.
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. Inside the case 11 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, which are arranged on the path and decelerate the drive rotation of the electric motors 2A and 2B, are arranged side by side on the same axis. 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. 2-10 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.

  Further, as shown in FIG. 3, an external communication pipe 49 for communicating the breather chamber 41 with the outside is fitted to the central case 11 </ b> M on the upper surface in the vertical direction of the breather chamber 41. The breather chamber side end portion 49a of the external communication pipe 49 is arranged so as to be directed downward in the vertical direction. Therefore, the oil is prevented from being discharged to the outside through the external communication pipe 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 medium pressure feeding 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 rectangular tube 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 as a reservoir for accommodating a strainer 71 described later and storing oil. The pair of overhanging portions 101 and 102 forming the strainer accommodating chamber 105 communicate with the through holes 107a and 107b communicating the left reservoir RL and the strainer accommodating chamber 105, and the right reservoir RR and the strainer accommodating chamber 105. A through hole (not shown) is formed. Thereby, the left reservoir RL and the right reservoir RR communicate with each other via the strainer storage chamber 105.

  The tip surfaces of the pair of overhanging portions 101, 102, the bottom wall 103, and the upper wall 104 constituting the strainer accommodating chamber 105 form a lid member fixing portion 105b, and are the outer edges of the front opening portion 105a that opens outward. Form. The front opening 105a of the strainer accommodating chamber 105 is closed by a lid member 72 to which the electric oil pump 70 is attached. The lid member 72 is provided with a case fixing portion 72 a having a substantially square end surface at a position facing the lid member fixing portion 105 b of the case 11.

  As shown in FIGS. 5 and 6, the electric oil pump 70 includes a plurality of case fixing portions 72 a formed in the lid member 72 and a plurality of lid member fixing portions 105 b formed in the front opening 105 a of the strainer accommodating chamber 105. The bolt 106 is fastened and fixed to the front opening 105 a of the strainer accommodating chamber 105. Therefore, the electric oil pump 70 is attached to the lid member 72 so as to be disposed outside the case 11 with respect to the lid member 72 in a closed state in which the lid member 72 is attached to the case 11 and closes the front opening 105a. ing. In the closed state, an oil passage forming cover 96 as a flow path forming member is detachably provided on the inner side of the case 11 with respect to the inner surface of the lid member 72 from the lid member 72. It is fixed to. The oil passage forming cover 96 together with the lid member 72 defines a part of the oil passage of the hydraulic circuit. 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. As shown in FIG. 10, solenoid valves 150 and 151 are attached to the side of the lid member 72 opposite to the oil passage forming cover 96, and the low pressure oil passage switching valve 73 and the brake oil passage switching valve are energized. Communicating / blocking the pilot oil passage provided between

  Further, the strainer 71 is detachably fixed only to the lid member 72 by inserting the drain port 71a into the lid member 72 and fastening the oil passage forming cover 96 with a bolt 69 that fastens to the lid member 72. Yes. 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.

Referring also to FIG. 7, the strainer 71 constituting 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 72 a of the lid member 72, and the suction port of the strainer 71 Is located in the oil in the strainer accommodating chamber 105 in the attached state where the lid member 72 is fixed to the case 11.
In addition, the electric oil pump 70 and the lid member 72 constitute an oil discharge passage 95, and the oil pumped by the pumping portion 87 of the electric oil pump 70 described later is interposed between the lid member 72 and the oil passage forming cover 96. Send to the formed hydraulic circuit.

  The oil passage forming cover 96 has a brake oil passage working chamber port 108a, which will be described later, formed on the outer peripheral surface of the central case 11M in the strainer accommodating chamber 105, and an oil passage for lubricating the portion to be cooled. Two outlet pipes 97a and 97b connected to the cooling / lubricating port 108b are attached.

  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.

  Returning to FIGS. 6 to 8, the electric oil pump 70 is disposed at a position lower in the vertical direction than the electric motor 90, an electric motor unit 85 that houses an electric motor 90 composed of a position sensorless brushless DC motor, and the electric motor 90. And a pumping unit 87 that accommodates the trochoid pump 86 driven by the motor. The electric oil pump 70 is controlled by PID control based on the target rotational speed and the like. The pressure feeding portion 87 is provided below the oil suction passage 94 and the oil discharge passage 95, and adjusts the discharge amount by rotating the inner rotor 86a connected to the rotating shaft 90a of the electric motor 90 and the outer rotor 86b, while adjusting the discharge amount. The oil flowing from 71 into the oil suction path 94 is discharged to the oil discharge path 95.

  The electric motor 90 has a rotor 91 and a stator 92, and a rotating shaft 90a of the electric motor 90 that externally fits the rotor 91 is a partition member fixed to the pump case main body 77 and the pump case main body 77 via bearings 89a and 89b. 78. In addition, a control member 88 is disposed above the partition member 78, and the electric motor 90 and the control member 88 are electrically connected by an electric wire 99 that passes through a communication hole 78 a formed in the partition member 78.

  As shown in FIGS. 8 and 9, the pump case main body 77 includes a rotor case 131 provided on the radially outer side of the outer rotor 86 b of the trochoid pump 86 and an upper case 132 positioned above the rotor case 131. And a lower case 133 positioned below the rotor case 131. Further, on each surface of the upper case 132 and the lower case 133 facing the rotor case 131, O-rings 134a and 134b are arranged in annular grooves 132a and 133a formed on the facing surfaces, and the annular grooves Annular leak recovery grooves 135a and 135b are formed inside 132a and 133a. Further, the rotor case 131 is formed with a leak recovery hole 131a that communicates the upper and lower leak recovery grooves 135a and 135b. The leak recovery hole 131 a communicates with a vertical hole 141 that extends downward from a drainage passage 140 (described later) formed in the upper case 132. Therefore, the oil leaked from the trochoid pump 86 is sent to the drainage path 140 from the leak recovery grooves 135a and 135b through the leak recovery holes 131a and the vertical holes 141 by the hydraulic pressure in the pump 86.

  Further, the electric oil pump 70 is provided with an oil seal 98 provided in the seal housing surface 132b of the upper case 132 between the lower bearing 89b and the trochoid pump 86 and in sliding contact with the outer periphery of the rotating shaft 90a. The The oil seal 98 partitions the trochoid pump 86 and the electric motor 90 and prevents oil from entering from the trochoid pump 86 side to the electric motor 90 side.

  Further, the upper case 132, the lid member 72, and the oil passage forming cover 96 are arranged on the trochoid pump 86 side of the oil seal 98 in the vertical direction, and the oil leaked from the trochoid pump 86 is discharged into the case 11. The above-described leak recovery hole 131a, leak recovery grooves 135a and 135b, the vertical hole 141, and the drainage path 140 are provided. Specifically, the drainage path 140 of the present embodiment is a middle position in the left-right direction between the oil suction path 94 and the oil discharge path 95 (see FIG. 10), and the seal housing surface 132b of the upper case 132 that houses the oil seal 98. It is formed so as to extend in the front-rear direction from the vicinity of the lower end.

  The drainage path 140 extends in the front-rear direction at substantially the same height in the upper case 132 and the lid member 72, and is connected to the oil path formation cover 96 at the joint surface between the lid member 72 and the oil path formation cover 96. It extends upward by a vertical groove 96a formed along the vertical direction. Further, although not shown, the drainage passage 140 passes through the oil passage formation cover 96 and opens into the strainer accommodating chamber 105 in the case 11.

  As a result, the most downstream end 140a, which is the open end of the drainage passage 140 on the case 11 side, has an upper and lower middle point C of the rotor 91 of the electric motor 90 and an oil seal 98 in the vertical direction as shown in FIG. (See also FIG. 8). Since the most downstream end portion 140a opens to the case 11 side at a position in the left-right direction different from the cross section shown in FIG. 11, the front-rear direction position and the vertical direction position of the most downstream end portion 140a are shown in FIG. Show. In FIG. 11, the line H represents the height of the fluid surface in the case 11.

  Here, the reason why the range between the upper and lower middle point C of the rotor 91 of the electric motor 90 and the oil seal 98 is set to the appropriate range P will be described. As shown in FIG. 12, if the most downstream end portion 140 a ′ of the drainage passage 140 is located above the upper and lower middle dividing point C of the rotor 91, the motor 90 will be used when a seal failure occurs in the oil seal 98. This causes the rotor 91 to be submerged to the height of the most downstream end portion 140a ', which increases the resistance during rotation and makes it impossible to exhibit the desired performance.

  On the other hand, as shown in FIG. 13, if the most downstream end 140 a ″ of the drainage passage 140 is located below the oil seal 98, the height of the fluid surface H is located in the appropriate range P. The oil seal 98 can be lubricated regardless of whether the oil seal 98 is good or bad. However, if the height of the fluid surface H is lower than the oil seal 98, the oil seal 98 is good again. Regardless of the defect, the oil seal 98 cannot be lubricated.

  Therefore, by disposing the most downstream end portion 140a of the drainage path 140 in the appropriate range P, the oil seal 98 can be lubricated by the leaked oil regardless of the height of the fluid surface H, In the unlikely event that a seal failure occurs in the oil seal 98 and oil enters the motor 90 side, more than half of the rotor 91 of the motor 90 will not be immersed, so the electric oil pump 70 can be driven continuously. .

  The drainage channel 140 may be opened directly from the lid member 72 into the case 11 if the most downstream end 140a is disposed in the appropriate range P in the vertical direction, or the drainage channel 140 and the oil It may be opened in the case 11 at the joint surface with the path forming cover 96, or may be further opened from the oil path forming cover 96 to the case 11 side. However, the most downstream end portion 140 a of the drainage passage 140 is formed on the joint surface between the lid member 72 and the oil passage formation cover 96, or the oil passage formation cover 96, so that the most downstream end portion 140 a becomes the lid member 72. The degree of freedom of arrangement is higher than in the case of forming the drainage path 140, and the drainage path 140 to the most downstream end 140a can be easily formed.

  Further, the fluid surface H in the case 11 is set to be lower than the vertical middle point C of the rotor 91 of the electric motor 90 in the vertical direction. Thereby, in the unlikely event that a seal failure of the oil seal 98 occurs, it is possible to reliably prevent more than half of the rotor 91 of the electric motor 90 from being immersed.

  As described above, according to the rear wheel drive device 1 of the present embodiment, the electric oil pump 70 includes the trochoid pump 86 that pumps oil and the electric motor 90 that drives the trochoid pump 86. The rotating shaft 90a is arranged perpendicular to the horizontal plane, and the trochoid pump 86 is arranged at a position lower than the electric motor 90 in the vertical direction. The electric oil pump 70 is disposed in sliding contact with the outer periphery of the rotating shaft 90a, and is disposed closer to the trochoid pump 86 than the oil seal 98, the oil seal 98 separating the trochoid pump 86 and the electric motor 90, and the trochoid pump. It further has a leak recovery hole 131 a for discharging oil leaked from the case 86 into the case 11, leak recovery grooves 135 a and 135 b, a drainage path 140, and a vertical hole 141. Further, the most downstream end portion 140 a that is the open end of the drainage passage 140 on the case 11 side is disposed between the upper and lower middle point C of the rotor 91 of the electric motor 90 and the oil seal 98 in the vertical direction. As a result, the oil seal 98 can be lubricated by the leaked oil in a normal state, and if the oil seal 98 is defectively sealed and the oil enters the motor 90 side, the rotor 91 of the motor 90 can be lubricated. Since more than half is not immersed, the electric oil pump 70 can be continuously driven.

  In addition, an oil passage forming cover 96 that is detachably attached to the inner surface of the lid member 72 is further provided, and the drainage passage 140 is formed across the electric oil pump 70, the lid member 72, and the oil passage forming cover 96, The downstream end portion 140 a is formed on the joint surface between the lid member 72 and the oil passage forming cover 96 or on the oil passage forming cover 96. Thereby, the arrangement | positioning freedom degree is higher than forming the most downstream end part 140a of the drainage path 140 in the cover member 72, and the drainage path 140 to the most downstream end part 140a can also be formed easily.

  Further, the case 11 has a strainer accommodating chamber 105 that stores oil inside the case 11, and the dynamic oil surface H in the strainer accommodating chamber 105 is the same as the dynamic oil surface H in the case 11 in the vertical direction. It is set lower than the upper / lower middle point C of the 90 rotors 91. Thereby, in the unlikely event that a seal failure of the oil seal 98 occurs, it is possible to reliably prevent more than half of the rotor 91 of the electric motor 90 from being immersed.

In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.
In the said embodiment, although the rotating shaft 90a of the electric motor 90 is arrange | positioned perpendicularly | vertically with respect to a horizontal surface, this invention is not limited to this, You may arrange | position so that it may incline with respect to a horizontal surface.

  In the above embodiment, the height setting of the most downstream end 140a of the drainage channel 140 has been described mainly. However, when the height of the fluid surface H is defined as the center, the height of the fluid surface H is defined. In addition, it is preferably arranged in the appropriate range P between the upper and lower middle point C of the rotor 91 of the electric motor 90 and the oil seal 98 in the vertical direction.

  That is, when the height of the hydraulic oil surface H is located above the upper and lower middle point C of the rotor 91, the rotor 91 of the electric motor 90 is positioned on the hydraulic oil surface H when a seal failure occurs in the oil seal 98. The oil will be immersed in the height, and the resistance during rotation will increase.

On the other hand, when the height of the dynamic oil surface H is located below the oil seal 98, when the most downstream end 140a of the drainage passage 140 is located in the appropriate range P, even if a defect occurs in the oil seal 98, Although the oil seal 98 can be lubricated, when the most downstream end 140a of the drainage passage 140 is located at a position lower than the oil seal 98, the oil seal 98 is lubricated regardless of whether the oil seal 98 is good or bad. I can't.
However, since the height of the fluid surface H can fluctuate violently depending on the behavior of the vehicle and the rotation of the motor, both the height of the fluid surface H and the most downstream end 140a of the drainage passage 140 are within the proper range P. Most preferably, it is set.

  In the above-described embodiment, the oil pump 70 is connected to the working chamber S of the hydraulic brake 60 and the cooled parts A1 and B1 or the lubricated parts A2 of the first and second electric motors 2A and 2B via each medium flow path. , B2 or the first and second planetary gear type speed reduction mechanisms 12A, 12B and the cooled parts or the lubricated parts which are at least one of the lubricated parts A3, B3. However, the present invention may be applied to a configuration in which the oil pump 70 supplies oil to either the working chamber S or the portion to be cooled.

  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 10, the first transmission is on the power transmission path between the left wheel and the first motor 2A, and the power transmission path between the right wheel and the second 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 (power unit)
2A 1st electric motor (power source)
2B Second electric motor (power source)
3 Vehicle 11 Case (housing)
12A First planetary gear reducer (power transmission mechanism)
12B Second planetary gear type speed reducer (power transmission mechanism)
60 Hydraulic brake (connection / disconnection means)
70 Electric oil pump (liquid medium pumping device)
72 Lid member (housing)
85 Electric motor part 86 Trochoid pump (pressure feeder)
87 Pumping section 90 Electric motor 96 Oil passage forming cover (separate member)
98 Oil seal (sealing member)
105 Strainer storage room (reservoir)
A1, B1 Cooled parts A2, B2, A3, B3 Lubricated part C Vertical middle point H Fluid surface LWr Left rear wheel (wheel)
RWr Right rear wheel (wheel)
S Working chamber

Claims (4)

A housing that houses at least one of a power source of the vehicle, and a power transmission mechanism disposed on a power transmission path between the vehicle wheel and the power source;
Provided in a detachable manner with respect to the casing, and is liquid in a cooled portion that is at least one of a cooled portion or a lubricated portion of the power source or a cooled portion or a lubricated portion of the power transmission mechanism. An electrically driven liquid medium pumping device for supplying a medium;
A power unit comprising:
The liquid medium pumping device includes a pumping body that pumps the liquid medium and an electric motor that drives the pumping medium, and is arranged so that a rotation shaft of the motor is perpendicular or inclined with respect to a horizontal plane. The body is arranged at a position lower in the vertical direction than the electric motor,
The liquid medium pumping device is disposed in sliding contact with the outer periphery of the rotating shaft, and is disposed on the pumping member side of the sealing member that partitions the pumping member and the electric motor, and from the pumping member. A drainage path for discharging the leaked liquid medium into the housing, and
The most downstream end, which is the open end of the drainage passage on the housing side, is arranged between the upper and lower middle points of the rotor of the electric motor and the sealing member in the vertical direction. apparatus. A hydraulically driven connection / disconnection means arranged on a power transmission path between a vehicle wheel and a power source, and switching the power transmission path between a cut-off state and a connection state;
A housing for accommodating the connecting / disconnecting means;
An electrically driven liquid medium pumping device that is detachably attached to the housing and supplies a liquid medium to the hydraulic chamber of the connecting and disconnecting means;
A power unit comprising:
The liquid medium pumping device includes a pumping body that pumps the liquid medium and an electric motor that drives the pumping medium, and is arranged so that a rotation shaft of the motor is perpendicular or inclined with respect to a horizontal plane. The body is arranged at a position lower in the vertical direction than the electric motor,
The liquid medium pumping device is disposed in sliding contact with the outer periphery of the rotating shaft, and is disposed on the pumping member side of the sealing member that partitions the pumping member and the electric motor, and from the pumping member. A drainage path for discharging the leaked liquid medium into the housing, and
The most downstream end, which is the open end of the drainage passage on the housing side, is arranged between the upper and lower middle points of the rotor of the electric motor and the sealing member in the vertical direction. apparatus. It further comprises a separate member that is detachably provided on the inner surface of the housing,
The drainage path is formed across the liquid medium pumping device, the housing, and the separate member,
3. The power plant according to claim 1, wherein the most downstream end is formed on a joint surface between the casing and the separate member or on the separate member. The case has a storage part for storing the liquid medium inside the case,
4. The power plant according to claim 1, wherein a dynamic oil surface of the storage unit is set to be lower than the vertical middle point in a vertical direction. 5.

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