JP2015082961A - Drive device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a drive device which enables housings to be positioned by positioning pins without dropping a filter attached to the positioning pin with the filter.SOLUTION: The drive device includes multiple positioning pins 151, 152 which position first housings 11A, 11B and a second housing 11M. At least the one positioning pin 152 forms a flow passage 156 in which a liquid fluid provided for lubrication and/or cooling passes. A filter 157 is attached to one end side of the positioning pin 152. A protruding length L1 of the positioning pin 152 with the filter, which protrudes from the housing 11M, is shorter than a protruding length L2 of the positioning pin 151 to which the filter is not attached.

Description

  The present invention relates to a drive device, and more particularly to a drive device including positioning pins for positioning a plurality of divided housings.

  Conventionally, there has been disclosed a cooling device for an electric motor in which the electric motor is housed in a plurality of divided housings and liquid refrigerant supplied from a pump having a strainer is discharged from the discharge port toward the electric motor to improve the cooling performance. (For example, refer to Patent Document 1).

JP 2013-13194 A

  However, the cooling device for an electric motor described in Patent Document 1 does not specifically describe the positioning configuration when assembling a plurality of divided housings or the flow path connection between the housings. Generally, positioning pins are frequently used for positioning a plurality of housings. For example, in assembling an electric motor housing, after aligning the axis of the rotating shaft and centering the housing, the housing is centered around the rotating shaft. The positioning pins were aligned and assembled while rotating. Further, in assembling a housing having a liquid fluid supply flow path, it is known to save space by forming a flow path in a positioning pin.

  In the supply flow path having such a configuration, in order to remove impurities in the liquid fluid, it is conceivable to provide a filter in the flow path of the positioning pin to form a positioning pin with a filter. However, when the housing is centered and fitted while rotating the housing in the circumferential direction around the rotation axis, one housing may come into contact with the filter of the positioning pin with a filter, and the filter may fall off. was there.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a drive device capable of positioning housings with positioning pins without dropping a filter mounted in a positioning pin with a filter. It is to provide.

In order to achieve the above object, the invention according to claim 1
A first housing (for example, described later) that accommodates a drive mechanism (for example, first and second electric motors 2A, 2B in the later described embodiment) having a predetermined center axis (for example, axles 10A, 10B in the later described embodiments) Side cases 11A, 11B) in the embodiment,
A second housing (for example, a central case 11M in an embodiment described later) fitted into the first housing from the central axis direction;
A plurality of positioning pins for positioning the first housing and the second housing (for example, positioning pins 151 and positioning pins 152 with a filter in embodiments described later);
A driving device (for example, a driving device 1 in an embodiment described later),
Among the plurality of positioning pins, at least one of the positioning pins (for example, the positioning pin with filter 152 in an embodiment described later) is a flow path (for example, a liquid fluid that is used for lubrication and / or cooling inside) A positioning pin with a filter (for example, a positioning pin with a filter in an embodiment to be described later) that constitutes a flow path 156 in an embodiment to be described later and that has a filter (for example, a filter 157 in an embodiment to be described later) attached to one end side 152),
When the plurality of positioning pins are inserted into one of the first housing or the second housing, a protruding length of the positioning pin with a filter protruding from the first or second housing (for example, implementation described later) The protruding length L1) in the embodiment is shorter than the protruding length of the positioning pin without the filter (for example, the protruding length L2 in the embodiment described later).

In addition to the configuration of claim 1, the invention according to claim 2
The drive mechanism is a rotating electrical machine (for example, first and second electric motors 2A and 2B in the embodiments described later),
The first housing includes a supply passage (for example, front horizontal oil passages 110A and 110B in an embodiment described later) for supplying the liquid fluid to the rotating electrical machine, and the liquid from the supply passage to the rotating electrical machine. A supply port for ejecting fluid (for example, discharge ports 112A and 112B in the embodiments described later),
The second housing includes a pump that supplies the liquid fluid to the supply flow path (for example, an electric oil pump 70 in an embodiment described later) and a strainer that captures impurities in the supply flow path (for example, implementation described later). A strainer 71) in the form,
The flow path of the positioning pin with filter is disposed on the downstream side of the pump, and the supply flow path is connected to the downstream of the flow path.

The invention according to claim 3 includes, in addition to the configuration of claim 1 or claim 2,
The filter is formed such that a maximum particle diameter that can pass through the filter is smaller than a diameter of the supply port.

  According to the first aspect of the present invention, the first housing and the second housing are rotated while rotating the first housing or the second housing in the circumferential direction in a state where the first housing and the second housing are centered. When fitting, the other of the first housing or the second housing can be prevented from coming into contact with the filter of the positioning pin with filter to prevent the filter from falling off, and the reduction in manufacturing efficiency can be suppressed.

  According to the second aspect of the present invention, impurities in the supply flow path are removed by the strainer, and the filter is disposed at the fitting portion between the first housing and the second housing that are located downstream of the strainer. And even if impurities are contained in the supply flow path downstream from the strainer at the initial operation of the pump, impurities can be removed by the filter, and the supply port is reliably prevented from being clogged with impurities. Can do.

  According to the invention of claim 3, it is possible to reliably prevent the supply port from being clogged with impurities.

1 is a block diagram showing a schematic configuration of a hybrid vehicle that is an embodiment of a vehicle on which a drive device according to the present invention can be mounted. It is a longitudinal cross-sectional view of a drive device. FIG. 3 is an enlarged partial cross-sectional view of an upper portion of the drive device shown in FIG. 2. It is a perspective view which shows the state in which the drive device of FIG. 1 was mounted in the flame | frame. It is a disassembled perspective view of the drive device of FIG. It is a side view which shows the assembly procedure of a drive device. It is sectional drawing in the AA line of FIG. 9, (a) is sectional drawing of the positioning pin provided with the flow path, (b) is sectional drawing of the positioning pin with a filter. It is a circuit diagram which shows a part of refrigeration flow path to which oil is supplied from a pump. It is a front view of the side case with which the electric motor was assembled | attached.

  The 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, a case where the driving device is used for driving the rear wheels will be described as an example, but it may be used for driving the 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. While power is transmitted to the front wheel Wf via the transmission 7, 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 and 2B of the rear wheel drive device 1 on the rear wheel Wr side are connected to the battery 9 to supply power from the battery 9 and to regenerate energy to the battery 9. Is possible. In FIG. 1, reference numeral 8 denotes a control device for controlling the entire vehicle.

First, a drive device according to an embodiment of the present invention will be described with reference to 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 sides of the central case 11 </ b> M so as to sandwich 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 electric motors 2A and 2B for driving the axles, and first and second shifts for decelerating the driving rotation of the electric motors 2A and 2B. First and second planetary gear type speed reducers 12A and 12B as machines 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 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 central 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 central case 11M constitute a second case 11R that accommodates the second electric motor 2B and the second planetary gear speed reducer 12B. The first case 11L includes a left reservoir RL that stores oil as a liquid medium that is used for lubrication and / or cooling of at least one of the first electric motor 2A and the power transmission path, and the second case 11R includes The second electric motor 2B and the right storage part RR that stores oil used for lubrication and / or cooling of at least one of the power transmission paths are provided. As shown in FIG. 4, the case 11 is supported by support portions 13 a and 13 b of a frame member 13 that is a part of a frame that is a skeleton of the vehicle 3 and a frame of the drive device 1 (not shown). The support portions 13a and 13b are provided on the left and right with respect to the center of the frame member 13 in the vehicle width direction. Moreover, the arrow in FIGS. 2-4 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 outside of the case 11 so that the air inside the case 11 escapes to the outside through the breather chamber 41 so that the air does not become excessively high temperature and pressure. Configured as follows. 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, 44 and the left and right dividing walls 45 that form the lower surface of the breather chamber 41 are such that the first cylindrical wall 43 is positioned radially inward from the second cylindrical wall 44, and the left and right dividing walls 45 are A third cylinder that extends from the inner end of the second cylindrical wall 44 to the inner end of the first cylindrical wall 43 while being bent while reducing the diameter, and further extends radially inward and extends substantially horizontally. Reach wall 46. The third cylindrical wall 46 is located on the inner side of both outer end portions of the first cylindrical wall 43 and the second cylindrical wall 44 and substantially in the center thereof.

  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, the stators 14A and 14B are fixed to the side cases 11A and 11B, respectively, and the annular rotors 15A and 15B rotate around the rotation axis X on the inner peripheral side of the stators 14A and 14B. Arranged to be possible. 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 radius, and the first and second electric motors 2A and 2B are arranged in mirror symmetry with each other. The axle 10A and the cylindrical shaft 16A pass through the first electric motor 2A and extend from both ends of the first electric motor 2A. The axle 10B and the cylindrical shaft 16B also penetrate the second electric motor 2B. , Extending from both ends of the second electric motor 2B.

  The first and second planetary gear speed reducers 12A and 12B include sun gears 21A and 21B, a plurality of planetary gears 22A and 22B meshed with the sun gear 21, and planetary carriers 23A that support these planetary gears 22A and 22B. , 23B and ring gears 24A, 24B meshed with the outer peripheral sides of the planetary gears 22A, 22B. The driving forces of the electric motors 2A, 2B are input from the sun gears 21A, 21B, and the decelerated driving forces are transmitted to the planetary carrier 23A, It is output to the axles 10A and 10B through 23B.

  The sun gears 21A and 21B are formed integrally with the cylindrical shafts 16A and 16B. Further, 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, a hydraulic brake 60 constituting braking means for the ring gear 24B is provided. It arrange | positions so that it may overlap with the 1st pinion 26B in radial direction, and it may overlap with the 2nd pinion 27B in an 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. These plates 35 and 36 are arranged to be 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 further provided with a receiving provided on the outer peripheral surface of the third cylindrical wall 46. The elastic member 39 supported by the seat 38 is constantly urged in a direction to release the fixed plate 35 and the rotating plate 36.

  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 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.

  In addition, as shown in FIG. 5, the outer peripheral surfaces of the first and second cylindrical walls 43 and 44 and the left and right dividing walls 45 of the central case 11M 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, 44 and the left and right dividing walls 45, a pair of projecting portions 101, 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 that accommodates a strainer 71 described later is formed. The strainer accommodating chamber 105 is closed by a lid member 72 to which the electric oil pump 70 is attached, and a strainer 71 is connected to the electric oil pump 70. The electric oil pump 70 is attached to the strainer accommodating chamber 105 by fastening and fixing the lid member 72 with a plurality of bolts 106.

  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 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 can be operated in at least two modes of a high pressure mode and a low pressure mode. It is controlled. Then, the oil used for lubrication and / or cooling is sucked and discharged from the strainer 71 while adjusting the discharge amount by rotating an inner rotor or an outer rotor (not shown).

  The strainer 71 is made of non-woven fabric, removes foreign matter in the oil sucked from a suction port (not shown) provided on the lower surface, and the oil from which the foreign matter has been removed is sent to the electric oil pump 70. .

  The discharge port of the electric oil pump 70 is connected to a working chamber port 108a that communicates with the hydraulic brake 60 and a cooling / lubricating port 108b that communicates with cooling channels 120A and 120B described later.

  The case 11 is formed with a brake fluid passage (not shown) that communicates from the working chamber port 108a to the working chamber S of the hydraulic brake 60, and vertically from the cooling / lubricating port 108b to the front of the central case 11M. The front vertical oil passage 109 extending in the direction, the left and right branches from the front vertical oil passage 109, and the front horizontal oil passages 110A, 110B extending in the horizontal direction in front of the cases 11A, 11B, 11M, and the cases 11A, 11B, respectively. Front and rear horizontal oil passages 111A and 111B extending rearward from the outer ends of the front horizontal oil passages 110A and 110B are formed.

  A plurality of discharge ports 112A and 112B for supplying oil to the coil side surfaces of the stators 14A and 14B are formed in the front-rear horizontal oil passages 111A and 111B (see FIG. 2), and extend downward to form the axles 10A and 10B. Lubricating oil passages 113A and 113B for supplying oil into the inside are connected. As shown in FIG. 2, the lubricating oil passages 113A and 113B communicate with the axial holes 114A and 114B formed in the axles 10A and 10B, and communicate with the oil passages 116A and 116B provided in the planetary carriers 23A and 23B. To do. Furthermore, the oil that has flowed out from the opening ends 118A and 118B of the axial holes 114A and 114B lubricates each part of the one-way clutch 50.

  Thus, the front vertical oil passage 109, the front horizontal oil passages 110A and 110B, the front and rear horizontal oil passages 111A and 111B, the discharge ports 112A and 112B, the lubricating oil passages 113A and 113B, the axial holes 114A and 114B, and the oil The paths 116A and 116B form refrigeration flow paths 120A and 120B that cool or lubricate each part.

  The front horizontal oil passages 110A and 110B branching from the front vertical oil passage 109 and extending in the horizontal direction abut the end surface 11Aa of the side case 11A and the end surface 11Ma on the side case 11A side of the central case 11M, and Horizontal oil provided in each case 11A, 11B, 11M by butting the end face 11Ba of the side case 11B and the end face 11Mb of the central case 11M on the side case 11B side (see FIG. 5) Paths 110a, 110b, and 110c (see FIG. 5) are formed in communication.

  As shown in FIGS. 6 to 9, the end surface 11Aa of the side case 11A and the end surface 11Ma on the side case 11A side of the center case 11M, and the end surface 11Ba of the side case 11B, and the center case 11M A positioning pin 151 for aligning the cases 11M, 11A, and 11B when the center case 11M and the side cases 11A and 11B are assembled with the end surface 11Mb on the side case 11B side. And the positioning pin 152 with a filter is provided. Since the connection structure between the central case 11M and the side case 11A and the connection structure between the central case 11M and the side case 11B are the same, the side case 11A side will be described below. The description on the side is omitted.

  Specifically, as shown in FIG. 7, the positioning pin 151 is a cylindrical member, and one end is fitted in a positioning hole 153 formed in the central case 11M, and the other end is in the central case 11M and the side case 11A. Is fitted into the positioning hole 161 formed in the side case 11A.

  The positioning pin 152 with a filter is a cylindrical member that forms a flow path 156 that penetrates in the axial direction, and is shorter than the positioning pin 151. One end of the positioning pin 152 with the filter is fitted into a stepped hole 158 formed by expanding the end of the horizontal oil passage 110c provided in the central case 11M, and the other end is lateral to the central case 11M. By assembling with the case 11A, the end of the horizontal oil passage 110a of the side case 11A is fitted into a stepped hole 162 formed by expanding the diameter.

  A filter 157 with which the edge portion 157a abuts is attached to the end face on the other end side of the positioning pin 152 with filter. The filter 157 is a filter having a substantially frustoconical mesh shape made of stainless steel wire, and the mesh size is such that the maximum particle diameter that can pass through the filter 157 is the discharge port 112A that supplies oil to the coil side surface of the stator 14A ( It is formed smaller than the aperture of (see FIG. 2). The diameter of the edge portion 157 a of the filter 157 is set to be equal to or smaller than the outer diameter of the positioning pin 152 with filter so as not to extend from the outer peripheral surface of the positioning pin 152 with filter.

  The positioning pin 152 with filter fits the stepped hole 158 with the substantially frustoconical tip 157 b of the filter 157 facing the back side of the stepped hole 158. That is, the tip 157b of the filter 157 is disposed on the upstream side of the front horizontal oil passage 110A. Thereby, the foreign matter mixed in the oil is not collected on the outer peripheral side of the filter 157 and the tip portion 157b is not blocked, and the flow rate can be secured over a long period of time.

  Further, as shown in FIGS. 6 and 7, the protruding length L1 of the positioning pin 152 with filter protruding from the end surface 11Ma of the central case 11M is set shorter than the protruding length L2 of the positioning pin 151 without a filter ( L1 <L2).

  Next, an assembly procedure between the central case 11M and the side case 11A (11B) will be described with reference to FIG. As shown in FIG. 6, first, the side case held at the upper side of the central case 11 </ b> M after the end surface 11 </ b> Ma of the central case 11 </ b> M is held with a jig (not shown) facing upward in the horizontal direction (the axis center is vertical) With the end surface 11Aa of 11A facing the end surface 11Ma, the center between the center case 11M and the side case 11A, specifically, the center axes CL1, CL2 of the first planetary gear type speed reducer 12A and the axle 10A Align and align the core.

  Then, the side case 11A is rotated in the circumferential direction around the center axis CL2, and the center of the positioning pin 151 without the filter is aligned with the center of the positioning hole 161 of the side case 11A. Do. Next, the side case 11A is lowered to engage the sun gear 21A of the cylindrical shaft 16A and the first pinion 26A, and the axle 10A protruding from the end surface 11Aa of the side case 11A is connected to the planetary gear of the first planetary gear type speed reducer 12A. A positioning pin 151 having a long projecting length L2 from the end surface 11Ma is inserted into the positioning hole 161 of the side case 11A and the side case 11A is further lowered to fit the carrier 29A, and the projecting length from the end surface 11Ma. The positioning pin 152 with a filter having a short L1 is fitted into the stepped hole 162.

  Thus, when fitting of the positioning pin 152 with filter and the stepped hole 162 is started, the first planetary gear type speed reducer 12A and the axle 10A, and the positioning pin 151 and the positioning hole 161 are fitted. Therefore, the center of the positioning pin 152 with filter and the stepped hole 162 also coincide. Therefore, the side case 11A and the filter 157 do not interfere with each other, and the filter 157 is reliably prevented from falling off from the positioning pin 152 with filter.

  FIG. 8 is a circuit diagram showing a part of the cooling flow path to which oil is supplied from the pump, and the oil sucked from the strainer 71 by the pump 70 passes through the front vertical oil path 109 and the horizontal oil path 110c. Oil is transferred from the discharge ports 112A and 112B to the coil side surfaces of the stators 14A and 14B after the foreign matter is removed by the filter 157 built in the filter-equipped positioning pins 152 and sent to the positioning pins 152 with filters of the side cases 11A and 11B. Supply.

  As described above, according to the driving apparatus 1 according to the present embodiment, the positioning pins 151 and the positioning pins 152 with the filter for positioning the side cases 11A and 11B and the central case 11M are provided. In addition, a flow path 156 through which a liquid fluid used for lubrication and / or cooling passes is formed, and a filter 157 is attached to one end side, and the protruding length L1 of the positioning pin 152 with filter protruding from the central case 11M is Since the protruding length L2 of the positioning pin 151 without the filter is shorter, the side cases 11A and 11B are rotated in the circumferential direction with the side case 11A or 11B and the center case 11M being centered. When the side cases 11A and 11B and the central case 11M are fitted together, the side cases 11A and 11B It is suppressed that would contact the filter 157 of the filter with the positioning pins 152, it is possible to suppress a decrease in manufacturing efficiency by preventing falling off of the filter 157.

  Further, the side cases 11A and 11B inject the liquid fluid into the cooling flow paths 120A and 120B for supplying the liquid fluid to the first and second electric motors 2A and 2B, and the first and second electric motors 2A and 2B. The central case 11M includes a pump 70 that supplies a liquid fluid to the cooling and cooling flow paths 120A and 120B, and a strainer 71 that traps impurities, and a positioning pin with a filter. The flow path 156 of the 152 is disposed on the downstream side of the pump 70, and the cooling flow paths 120A and 120B are connected to the downstream of the flow path 156. Therefore, the strainer 71 removes impurities in the supply flow path. A filter 157 is disposed at a fitting portion between the side cases 11A and 11B and the central case 11M which are located downstream of the strainer 71. 2 When the electric motors 2A, 2B and the pump 70 are initially operated, even if impurities are contained in the cooling flow paths 120A, 120B downstream of the strainer 71, the impurities can be removed by the filter 157, and the discharge port 112A 112B can be reliably prevented from being clogged with impurities.

  Further, the filter 157 is formed so that the maximum particle diameter that can pass through the filter 157 is smaller than the diameter of the discharge ports 112A and 112B, so that it is ensured that the discharge ports 112A and 112B are clogged with impurities. Can be prevented.

  In the above embodiment, the projecting lengths L1 and L2 from the end surface 11Ma are made different by using positioning pins 151 and 152 having different lengths. However, the positioning pins 151 and 152 having the same length are used for positioning. Different protrusion lengths L1 and L2 may be provided by making the depths of the hole 153 and the stepped hole 158 different.

In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.
The number of the positioning pins 151 and the positioning pins 152 with a filter of the present invention may be at least one each, and is arbitrarily set according to the positioning accuracy, the hole processing accuracy, and the number of flow paths.
Further, although the hybrid vehicle has been described as the application vehicle, the present invention is not limited to this, and may be, for example, an electric vehicle using only a motor as a drive source.

DESCRIPTION OF SYMBOLS 1 Drive device 2A 1st electric motor (drive mechanism, rotary electric machine)
2B Second electric motor (drive mechanism, rotating electric machine)
10A, 10B Axle (center axis)
11A, 11B Side case (first housing)
11M center case (second housing)
70 Electric oil pump (pump)
71 Strainer 110A, 110B Front horizontal oil passage (supply passage)
112A, 112B Discharge port (supply port)
120A, 120B Cooling channel (supply channel)
151 Positioning pin 152 Positioning pin with filter 156 Flow path 157 Filter L1 Projection length of positioning pin with filter L2 Projection length of positioning pin without filter

Claims (3)

A first housing that houses a drive mechanism having a predetermined central axis;
A second housing fitted into the first housing from a central axis direction;
A plurality of positioning pins for positioning the first housing and the second housing;
A drive device comprising:
Among the plurality of positioning pins, at least one of the positioning pins constitutes a flow path through which a liquid fluid used for lubrication and / or cooling passes, and has a filter mounted with a filter on one end side. Pin,
When the plurality of positioning pins are inserted into one of the first housing or the second housing, the protruding length of the positioning pin with filter protruding from the first or second housing is attached to the filter. A drive device characterized by being shorter than the protruding length of the positioning pin which is not. The drive mechanism is a rotating electric machine,
The first housing includes a supply channel for supplying the liquid fluid to the rotating electrical machine, and a supply port for injecting the liquid fluid from the supply channel to the rotating electrical machine,
The second housing includes a pump that supplies the liquid fluid to the supply flow path, and a strainer that traps impurities in the supply flow path.
2. The driving device according to claim 1, wherein the flow path of the positioning pin with a filter is disposed on the downstream side of the pump, and the supply flow path is connected to the downstream of the flow path. 3. The drive device according to claim 1, wherein the filter is formed so that a maximum particle diameter that can pass through the filter is smaller than a diameter of the supply port. 4.

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