WO1997023362A1 - Dispositif d'entrainement pou automobiles electriques - Google Patents
Dispositif d'entrainement pou automobiles electriques Download PDFInfo
- Publication number
- WO1997023362A1 WO1997023362A1 PCT/JP1996/003752 JP9603752W WO9723362A1 WO 1997023362 A1 WO1997023362 A1 WO 1997023362A1 JP 9603752 W JP9603752 W JP 9603752W WO 9723362 A1 WO9723362 A1 WO 9723362A1
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- WO
- WIPO (PCT)
- Prior art keywords
- oil
- motor
- gear
- chamber
- case
- Prior art date
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K1/00—Arrangement or mounting of electrical propulsion units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0447—Control of lubricant levels, e.g. lubricant level control dependent on temperature
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0409—Features relating to lubrication or cooling or heating characterised by the problem to increase efficiency, e.g. by reducing splash losses
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
- F16H57/0423—Lubricant guiding means mounted or supported on the casing, e.g. shields or baffles for collecting lubricant, tubes or pipes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
- F16H57/0426—Means for guiding lubricant into an axial channel of a shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0427—Guidance of lubricant on rotary parts, e.g. using baffles for collecting lubricant by centrifugal force
- F16H57/0428—Grooves with pumping effect for supplying lubricants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/045—Lubricant storage reservoirs, e.g. reservoirs in addition to a gear sump for collecting lubricant in the upper part of a gear case
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0457—Splash lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0476—Electric machines and gearing, i.e. joint lubrication or cooling or heating thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0482—Gearings with gears having orbital motion
- F16H57/0483—Axle or inter-axle differentials
Definitions
- the present invention relates to a drive unit for an electric vehicle, and more particularly to a lubrication unit for a drive unit for an electric vehicle that combines a motor and a gear unit that transmits the power to wheels.
- One form of electric vehicle drive is a combination of a motor and a gear that transmits the power to the wheels.
- the gears must be lubricated regardless of whether the motor is air-cooled or oil-cooled.
- the oil level in the gear case It must be high enough to immerse the entire differential gear case in oil.
- the lubricating oil is sufficiently distributed to each part of the gear, it is not necessary to increase the oil level in the gear case as described above. In order to reduce it, it is necessary to reduce it to the necessary minimum level. Under these circumstances, according to the technology disclosed in U.S. Pat. No. 5,295,413, an oil reservoir is provided at the top of a gear case, and oil is supplied to and discharged from the reservoir. The oil level is adjusted.
- the oil reservoir is provided in the gear case, so that in addition to the space necessary for accommodating the gear portion, the oil reservoir is provided.
- the gear case becomes large, and the weight of the drive unit increases accordingly.
- the present invention provides an electric vehicle that has a lightweight and compact configuration that does not require a separate oil reservoir, and that can reduce the agitation loss of the gear portion when the vehicle is running while securing the amount of lubricating oil when the vehicle is stopped.
- the primary purpose is to provide a driving device for the vehicle.
- a second object of the present invention is to make it possible to circulate oil to achieve the above object without generating a drive port for the oil circulation.
- a third object of the present invention is to maintain the oil level in the motor chamber during running of the vehicle at an appropriate level, and to cool the motor while preventing stirring loss due to rotation of the motor. Disclosure of the invention
- the present invention provides a motor comprising a stay, a rotor having a rotatable shaft rotating within the stay, and a rotation of the mouth-shaft to a wheel.
- a transmission section ; and a case for housing the motor and the gear section, the case having a partition separating a motor chamber for storing the motor and a gear chamber for storing the gear section,
- the partition has an orifice communicating the lower part of the motor chamber and the gear chamber, and a supply means for supplying oil in the gear chamber to the motor chamber in accordance with rotation of the gear part. It is characterized by having.
- the oil in the gear chamber is supplied to the motor chamber by the supply means in accordance with the rotation of the motor or the gear section during running of the vehicle. Then, the oil supplied to the motor chamber is returned to the gear chamber through the orifice of the partition wall. At this time, since the amount of oil supplied to the gear chamber by the supply means is larger than the amount of oil returned to the gear chamber through the orifice, the oil stays in the gear chamber, and the oil level in the gear chamber is reduced. descend. On the other hand, when the vehicle stops, the motor and the rotation of the gear section stop, so the supply means is The oil in the gear chamber is no longer supplied to the motor chamber, but the oil in the motor chamber continues to return to the gear chamber through the orifice in the bulkhead.
- the oil in the motor chamber decreases and the oil level in the gear chamber increases. Therefore, when the vehicle is running, the oil level in the gear chamber is lowered to reduce the agitation loss in the gear section, and when the vehicle is stopped, the oil level in the gear chamber is raised so that the gear section is prepared for starting. Lubricating oil amount can be secured. Therefore, the motor chamber can be used as an oil reservoir, and there is no need to provide an oil reservoir in the gear chamber, and the gear case can be made compact. Furthermore, since oil can be stored in the motor chamber when the vehicle is running, oil can be cooled while the stay is immersed in the oil so that the cooling effect of the motor can be enhanced.
- the supply means has an oil receiver that collects oil in a gear chamber lifted up by rotation of the gear unit and guides the oil to the motor chamber. Is done.
- the oil in the gear chamber which is pumped up by the rotation of the gear section, is collected by an oil receiver and supplied to the motor chamber, so that the structure of the supply means is simplified and the electric vehicle Drive device can be compact.
- a window is formed above the orifice of the partition wall and at the same level as the lowermost position on the peripheral surface of the rotor to communicate the motor chamber and the gear chamber.
- a window is provided above the orifice of the partition wall and at the same level as the lowermost position on the peripheral surface of the rotor, so that the motor chamber and the gear chamber are communicated with each other.
- the oil is returned to the gear chamber from the window shortly before the rotor is immersed. Therefore, by opening the window, the oil level in the motor room can be set to a level that does not allow the mouth to immerse, and it is possible to prevent the rotor from stirring while cooling the motor.
- FIG. 1 is an axially expanded sectional view of an electric vehicle drive device according to one embodiment of the present invention
- FIG. 2 is a view taken in the direction of arrows AA in FIG. 1
- FIG. (A) An axial cross-sectional view of the rotor and the stay showing the oil passage arrangement in the overnight
- FIG. 4 is a perspective view showing the oil receiver of the supply means in this drive unit in detail
- FIG. 6 is a cross-sectional view taken along the line BB in FIG. 5
- FIG. 7 is a cross-sectional view taken along the line C-C in FIG.
- FIG. 8 is a view taken in the direction of the arrow D--D in FIG. 5, FIG.
- FIG. 9 is a view taken in the direction of the arrow E--E in FIG. 5, and FIG. 10 is a partial modification of the supply means of the second embodiment.
- FIG. 4 is a partial sectional view in the axial direction of FIG. BEST MODE FOR CARRYING OUT THE INVENTION
- FIGS. 1 to 4 show a first embodiment of the present invention.
- this drive device has a stay 4 and a mouth shaft 2 which rotates in the stay 4.
- a motor housing composed of the rotor 3, a gear section 9 for transmitting the rotation of the mouth shaft 2 to wheels (not shown), and a case for accommodating the motor 1 and the gear section 9. 0 and the gear case 90 are combined).
- the case has a partition wall 12 that separates a motor chamber m that stores the motor 1 and a gear chamber g that stores the gear portion 9.
- the partition wall 12 includes a lower portion of the motor chamber m and a gear chamber g.
- An orifice 53 is formed, which communicates with the motor unit m.
- the supply means 5 has an oil receiver 51 that collects oil in the gear chamber g that is pumped up by the rotation of the gear unit 9 and guides the oil to the motor chamber m.
- a window 52 that connects the motor chamber m and the gear chamber g is located above the orifice 53 of the partition wall 12 and at the same level as the lowermost position of the peripheral surface of the rotor 3 of the motor 1. Is formed.
- FIG. 1 One-side shaft 2 rotatably supported at both ends in bearing case 10 via bearings 11 1 and a plurality of permanent magnets 3 corresponding to the number of poles fitted non-rotatably on the one-side shaft 2
- the core is fitted around the outer periphery of the rope and the core around the outer periphery of the rope, and the core is fitted to the outer case around the outer case with a key.
- a stator 4 having a coil end 41 extending from both ends of the core 40 in the axial direction.
- reference numeral 6 denotes a resolver attached to one end of the rotor shaft 2 for detecting a magnetic pole position from the rotation of the rotor shaft 2 for motor control by a member.
- the gear section 9 is composed of a counter gear mechanism and a differential mechanism to reduce the rotation of the mouth shaft 2 of the motor 1 and amplify the torque and transmit the same to the wheels in the same direction.
- the counter gear mechanism includes a counter shaft 93 supported at both ends by a gear case 90 via bearings, and an output fixed to one end of the shaft and fixed to one end of the motor shaft 1 of the motor 1 It comprises a large-diameter gear 92 that meshes with the gear 91 and a small-diameter gear 94 that is integrally formed on the other end of the counter shaft 93.
- the differential mechanism includes a differential gear composed of a well-known bevel gear, a differential case 96 for housing the differential gear, and a ring gear 95 fixed to the case 96 and engaged with the gear wheel 94. Both ends of the differential case 96 are supported by the gear case 90 via bearings.
- the differential gear in the differential case 96 is connected to left and right axles (not shown) via a universal joint.
- the motor case 10 and the gear case 90 that respectively house the motor 1 and the gear unit 9 having such a configuration are connected to each other and integrated.
- the positional relationship between the motor 1 and the gears of the gear section 9 integrated as described above is as shown in FIG. 2, and the position of the motor case 10 is slightly shifted from the position of the gear case 90. ing.
- the positions of the gears are schematically indicated only by outlines indicating their outer shapes.
- the supply means 5 in this embodiment is inserted into one end of the shaft oil passage 22 of the rotor shaft 2 from the side of the gear case 90 connected to the motor case 10. It comprises an oil supply pipe 50 and an oil receiver 51 connected to the opposite end of the gear case 90 side.
- the oil supply pipe 50 is bent in an L shape, and the vicinity of the bent portion is supported by the case, and the opposite end is mounted and supported on the case 90 via the oil receiver 51.
- the oil passage in motor shaft 1 is formed in shaft shaft 2, and is formed in shaft oil passage 22 and radial oil passage 23 connected to it, and core 30. And a connecting oil formed on the plate 21 and communicating with the radial oil passage 23 of the shaft 1 and the axial oil passage 3 2 of the core 30. Oil hole 25, which communicates with the passage 24, the axial oil passage 32 of the core 30, and opens radially inward of the coil end 41 of the stay 4, and the oil inside the shaft of the rotor shaft 2. And supply means 5 for supplying oil to the passage 22 (see FIGS. 1 and 2).
- the oil receiver 51 has a box shape having an open upper surface, and includes a ring gear 95 shown in FIG.
- the corners at the diagonal positions are cut out so as to reliably collect the oil pumped up by their rotation while avoiding interference with the outer periphery.
- the oil receiver 51 is moved closer to the outer periphery of the ring gear 95 and the large-diameter gear 92 so as to alternately straddle the outer periphery of the two gears 95, 92, and the collected oil So that the oil can be introduced into the shaft oil passage 22 of the rotor shaft 2 via the refueling pipe 50 without using special feeding means so that the oil can be collected at the same level as the shaft center of the shaft ⁇ oil passage 22. It is positioned at a predetermined height and is fixed to the case 90.
- the motor case 10 and the gear case 90 are connected to each other by a window 52 formed in an end wall of the gear case 10, and the lower edge of the window 52 is Acting as a weir that keeps the oil level on the motor case 10 side of the oil collected below the motor case 10 below the outer circumference of the rotor 3 indicated by the dotted line in the figure, the motor case 10 Can function as an oil reservoir.
- the two cases 10 and 90 are communicated with each other through a small-diameter orifice 53 formed below the window 52, and the orifice 53 is used to collect oil under the motor case 10. In the stopped state, the recovered oil gradually escapes to the gear case 90 side to perform the function of balancing the oil levels of both cases.
- the oil that serves both of lubrication and cooling is mainly contained in the gear case 90 up to the level Lm indicated by the middle dotted line in FIG. Therefore, in this state, the oil level for the start that requires a larger amount of lubrication in the gear section 9 than during normal running is secured.
- the ring gear 95 driven thereby rotates counterclockwise in FIG. 2, and the large-diameter gear 92 of the counter shaft rotates clockwise.
- the oil thus raised is collected in the oil reservoir 51.
- the collected oil is led to the oil supply pipe 50 and is supplied from the gear case 90 side into the in-shaft oil passage 22 of the mouthpiece shaft 2 o
- FIG. 3 the flow of oil on the motor side is indicated by arrows, and the oil supplied to the in-shaft oil passage 22 of the rotor shaft 2 as described above is generated by the rotation of the shaft 1 Due to the centrifugal force, the oil flows along the peripheral surface of the in-shaft oil passage 22, enters the respective undesired oil passages 23, passes through the connecting oil passage 24 of the plate 21, and passes through the axial oil passage 32 of the core 30.
- Each of the coil ends 4] is sprayed from the oil holes 25 of the plate 21 by centrifugal force of the rotor 3. Therefore, when the oil flows through the oil passage 32 in the axial direction of the core 30 in one way, it cools the core 30 reliably and is discharged from the oil hole 25, and the coil ends 4 at both ends of the stay 4 Supplied to one to ensure they cool.
- the oil that has cooled the motor in this way travels through the motor case 10 or drops from each part and collects below the motor case 10, and the amount exceeding the lower surface level of the window 52 becomes the gear case 9.
- the oil collected in the motor case 10 on the side opposite to the gear case with the core 40 sandwiched between the core 40 and the motor case The motor case 10 is guided to the window 52 side by using an unused groove among a plurality of key grooves formed in the motor case 10 so that the motor case 10 is prevented from rotating. In this way, during the operation of the motor, the oil level in the gear case 90 drops to the level L1 indicated by the dotted line at the bottom of FIG.
- the fall level in evening case 10 is kept at the level L h indicated by the dotted line at the top, which can cool stage 4 to the maximum without being stirred by the rotation of mouth 3. Then, when the operation of the motor 1 is stopped, the two oil levels gradually balance with the oil flowing through the orifice 53, and eventually reach the level Lm indicated by the dotted line in the middle of the figure.
- the lower portion of the motor case 10 is used as an oil reservoir while the vehicle is running, and the gear portion 9 is used in preparation for starting the vehicle when the vehicle is stopped.
- the orifice 53 at the bottom of the motor case 10 to return the oil, the oil level of the gear section 9 is reduced during running of the vehicle to reduce gear agitation loss.
- the stay 4 and its coil end 41 can be immersed in oil, and the cooling efficiency of the motor 1 can be improved.
- the orifice 53 transfers oil from the motor 1 to the gear section 9 and raises the oil level of the gear section 9 to ensure lubrication when starting.
- FIGS. 5 to 9 show a second embodiment of the present invention.
- the distance between the shaft of the rotor shaft 2 and the shaft of the differential gear is reduced as much as possible.
- the motor case and gear case, which were separated in the form, are integrated in this form to achieve weight reduction. Therefore, this embodiment is similar to the previous embodiment in the schematic configuration, but there are some differences in the detailed configuration due to the change in the case configuration.
- portions substantially corresponding to those of the first embodiment will be denoted by the same reference numerals, and the description will be mainly given to the differences.
- the motor shaft 1 and the gear unit 9 housed in the integrated case body 1 OA have the rotor shaft 2 of the motor shaft 1 and the differential case 9 6 And a position substantially above the differential gear axis. Then, as shown in FIG. 5, the motor room m side of the case 1OA is closed by the front case 10C, and the gear chamber g side is closed by the rear case 10B. As a result, the shaft 2 of the motor 1 is rotatably supported at both ends by the case body 1OA and the front case 10C via the bearings 11.
- the counter shaft 93 and the opposite ends of the differential case 96 are supported by the case body 10A and the rear case 10B via bearings, and are splined to the differential gears in the differential case 96.
- One yoke shaft 97 (shown by imaginary lines in FIG. 5) is connected at one end to the shaft of the differential case 96 and at the other end to bearings 13 and 14 directly.
- Main body 1 Supported by OA.
- the axial positional relationship between the large-diameter gear 92 and the small-diameter gear 9 in the counter gear mechanism is reversed with respect to the arrangement of the first embodiment, whereby the position of the differential mechanism is also reduced. It has been moved to the 1 side, and it has achieved axial compactness.
- the supply means 5 is formed using a case wall over the case main body 10 A and the lya case 10 B, and a partition wall of the case main body 10 A is provided. 12 between the end surface 1 2a side and the mating surface of the case body 10 A of the lya case 10 B with a width substantially equivalent to the distance between the surfaces, and above the peripheral surface of the gear 95.
- the formed oil receiver 51 and the oil supply pipe 50 inserted from one side of the rear case 10 B to one end of the in-shaft oil passage 22 of the mouth shaft 2 a to 50 c.
- the oil passage 50a in the case constitutes a pump discharge passage using the ring gear 95 as the gear of the gear pump, so to speak, an oil passage whose width is the same as that of the oil receiver 51 and whose oil passage area decreases as it goes upward. It is said that.
- the oil receiver 51 has a bottom wall that is a flat surface located above and near the peripheral surface of the ring gear 95, one side wall being one side surface of the oil passage 50 a in the case, and the other side wall.
- a small-volume wedge-shaped oil reservoir having an arc-shaped surface along the outer periphery of the shaft support bearing 11 of the output gear 91 fitted on the outer periphery of the rotatable shaft 2 is formed.
- a small diameter oil hole 51 a is formed in the bottom wall of the oil receiver 51, and the oil hole 51 a is formed in a lubricating oil passage of one bearing 16 supporting the differential case 96. They are connected by a route not shown.
- the oil passage 5 Ob in the case is formed as an oil passage having a rectangular cross section extending in the axial direction from the level above the oil receiver 51 in the rear case 10 B, and a radial oil passage 50 c having a circular cross section.
- the shaft extends to the shaft end of the rotatable shaft 2, is fitted therein, and is connected to the in-shaft oil passage 22 by a refueling pipe 50 fixed by a retaining plate 50 ′.
- the spring gear 15 a snapped on the inner periphery of the shaft end of the output gear 91 and the opening and closing shaft 2
- Oil feeding means utilizing rotation of a spiral thread of a coil spring 15 disposed in a compressed state between the shaft end and the shaft end is provided.
- the lower part of the gear chamber g is considerably widened in the axial direction from the width of the ring gear 95 in order to secure an oil reservoir.
- a pair of side plates 54, 55 are attached along the outer peripheral sides of both sides of the case, and these are composed of an annular press plate separate from the case body 1OA and the lya case 10B. As shown in Fig. 6 and Fig. 8, the upper part that does not significantly affect the lifting effect is cut out in the circumferential direction, and the case body 1 OA is tightened by bolts. And Lya case 10B are attached.
- the oil passages in M1 are essentially the same as those in the previous embodiment, but they are slightly different in the structure of the pongs.
- the oil passages in the shaft The strange direction oil passage 23 communicating with 22 is provided only on one side of the core 30, and it is connected to the axial oil passage 3 2 of the core 30 via the connecting oil passage 2 of the plate 21.
- the oil hole 25 opens radially inward of the coil end 41 of the stay 4.
- the case Using the connection space created by the formation of the gear chamber g and the gear chamber g, the lower part of the front case 10C is mainly formed to protrude below the end of the motor chamber m. Oil pool 5 6 is secured.
- the motor chamber m and the gear chamber g communicate with each other via a window 52 formed in a partition wall 12 on the end face 12 a side of the case body 10.
- the lower edge of the window 52 keeps the oil level of the oil collected under the motor chamber m on the motor chamber m side at the lowest point on the outer circumference of the rotor 3 indicated by the dotted line in the figure. It acts as a weir and allows the lower part of the motor chamber m to function as an oil reservoir.
- the lower surface of the window 52 is inclined. This inclination takes into consideration the traveling of the vehicle on an uphill road when the device is mounted on the vehicle.
- the motor chamber m and the gear chamber g are provided with windows 5 formed in the partition wall 12 on the peripheral surface 12 b side of the case body 108 and the partition wall 12 on the end surface 12 a side. It is communicated with a small-diameter orifice 53 formed at a level position below 2 (see Fig. 9). The operation of the orifice 53 is the same as that of the previous embodiment. With the oil collection below the motor chamber m stopped, the collected oil gradually escapes to the gear chamber g side. It is to balance the oil level in the chamber.
- a second return oil of another system parallel to the first return oil passage is provided. Roads are provided.
- the first return oil passage extends along the lowermost part of the stay overnight, extends the case body outward, and extends in the axial direction along the stay overnight. It is configured as a return oil passage 50 d.
- the second return oil passage is configured as an oil passage passing through the yoke shaft 97 accommodating portion of the universal joint in the gear chamber g, and the bearings 13 and 1 supporting both ends of the yoke shaft 97 are provided.
- the oil after cooling the motor 1 travels through the case body 1 OA or drops from each part and collects below the case body 1 OA as in the previous embodiment.
- the flow passes through the return oil passage, and the portion exceeding the lower surface level of the window 52 returns to the gear chamber g side.
- the oil collected in the case body 10A on the side opposite to the gear chamber with the core 40 interposed therebetween is guided to the window 52 side through the oil passage 50d, and similarly returns to the gear chamber g side. .
- the oil flows through the above-mentioned oil passages, etc., so that the oil level in the gear chamber g drops to the level L 1 indicated by the dotted line at the bottom of FIG.
- the oil level in the OA keeps the level Lh indicated by the dotted line at the top, which can cool the stage 4 to the maximum without being agitated by the rotation of the rotor 3.
- the shaft end of the counter shaft 93 located at substantially the same level as the window 52 is attached to the end face 1 of the bulkhead 12.
- An opening is provided through 2a, and the oil returning to the gear chamber g through this opening lubricates the bearing of the power shaft 93.
- the oil in the oil receiver 51 is returned from the oil hole 51a of the bottom wall to the gear chamber g via the bearing 16 and the oil in the motor chamber m is stopped.
- the oil in the oil reservoir 56 passes through the orifice 53 and returns to the gear chamber g as the flow of the second return oil passage.
- the oil that has passed through the orifice 53 returns to the gear chamber g through the end of the gear chamber g, the oil passage 50e, the accommodation portion of the yoke shaft 97, and the oil passage 50f, and returns to the gear chamber g. Gradually balances out, and eventually reaches the level L m indicated by the dotted line in the middle part of the figure.
- the same effect as in the previous embodiment can be obtained, but in addition, the advantage that the oil collecting effect of the oil receiver 51 is improved. Is obtained.
- the lower surface of the window 52 is inclined forward, the level of the lower surface of the window 52 is maintained substantially constant even on an uphill road, and the effect of the front-rear inclination of the vehicle on the oil level is eliminated. be able to.
- the oil temperature sensor 7 is installed in the oil sump 56 of the motor room m to detect the temperature, the motor load at each point can be accurately grasped from the actual oil temperature after cooling the motor. There is also an advantage that the motor control can be performed.
- FIG. 10 shows a modification in which the supply means 5 in the second embodiment is all integrated with a case.
- the portion corresponding to the oil passage pipe 50 constituting the oil passage of the supply means 5 in the previous embodiment is integrated with the lya case i 0 B, extends from the end of the lya case 10 B, and has the shaft of the output gear 91. It is configured as 50 g of a tubular oil passage inserted into the hole.
- the spring 15 is formed by directly displacing a snap ring fitted to the shaft hole with the position shifted from the end of the shaft hole of the output gear 91 to the end face of the tubular oil passage 50 g inside the spring seat 1. 5a.
- Such a configuration is effective in narrowing the gap between the outer periphery of the tubular oil passage 50 g and the shaft hole of the output gear 91 to reduce oil leakage from the supply oil passage. Since the road pipe 50 and its holding plate 50 ′ can be eliminated, the number of parts is reduced and
- the supply means may be constituted by an oil pump driven by rotation of a motor or a gear portion.
- the electric vehicle drive device is useful as a drive device for various vehicles, and is particularly suitable for use as a drive device mounted on an electric vehicle in an on-board format.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Motor Or Generator Cooling System (AREA)
- General Details Of Gearings (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/849,667 US5821653A (en) | 1995-12-21 | 1996-12-24 | Drive apparatus for electric vehicle |
DE69623111T DE69623111T2 (de) | 1995-12-21 | 1996-12-24 | Antriebsvorrichtung für elektrische kraftfahrzeuge |
EP96942618A EP0811521B1 (en) | 1995-12-21 | 1996-12-24 | Drive device for electric motorcars |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP34901395 | 1995-12-21 | ||
JP7/349013 | 1995-12-21 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1997023362A1 true WO1997023362A1 (fr) | 1997-07-03 |
Family
ID=18400905
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1996/003752 WO1997023362A1 (fr) | 1995-12-21 | 1996-12-24 | Dispositif d'entrainement pou automobiles electriques |
Country Status (4)
Country | Link |
---|---|
US (1) | US5821653A (ja) |
EP (2) | EP0811521B1 (ja) |
DE (1) | DE69623111T2 (ja) |
WO (1) | WO1997023362A1 (ja) |
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-
1996
- 1996-12-24 WO PCT/JP1996/003752 patent/WO1997023362A1/ja active IP Right Grant
- 1996-12-24 DE DE69623111T patent/DE69623111T2/de not_active Expired - Lifetime
- 1996-12-24 EP EP96942618A patent/EP0811521B1/en not_active Expired - Lifetime
- 1996-12-24 EP EP02003107A patent/EP1229270A3/en not_active Withdrawn
- 1996-12-24 US US08/849,667 patent/US5821653A/en not_active Expired - Lifetime
Patent Citations (4)
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JPS5452265A (en) * | 1977-10-03 | 1979-04-24 | Daihatsu Motor Co Ltd | Lubrication apparatus for transmission |
JPH03150050A (ja) * | 1989-11-07 | 1991-06-26 | Aisin Aw Co Ltd | 車両用モータの冷却装置 |
US5295413A (en) | 1992-10-14 | 1994-03-22 | General Motors Corporation | One-piece power transmission casing and a method of assembling a transmission mechanism therein |
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Title |
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Also Published As
Publication number | Publication date |
---|---|
US5821653A (en) | 1998-10-13 |
DE69623111D1 (de) | 2002-09-26 |
DE69623111T2 (de) | 2003-05-08 |
EP1229270A3 (en) | 2003-08-13 |
EP0811521A4 (en) | 1999-06-02 |
EP1229270A2 (en) | 2002-08-07 |
EP0811521A1 (en) | 1997-12-10 |
EP0811521B1 (en) | 2002-08-21 |
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