WO2015030024A1 - 動力伝達装置 - Google Patents
動力伝達装置 Download PDFInfo
- Publication number
- WO2015030024A1 WO2015030024A1 PCT/JP2014/072356 JP2014072356W WO2015030024A1 WO 2015030024 A1 WO2015030024 A1 WO 2015030024A1 JP 2014072356 W JP2014072356 W JP 2014072356W WO 2015030024 A1 WO2015030024 A1 WO 2015030024A1
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- WIPO (PCT)
- Prior art keywords
- drive pinion
- pinion gear
- refrigerant
- gear
- power transmission
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- 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
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/037—Gearboxes for accommodating differential gearings
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- 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
Definitions
- the present invention relates to a power transmission device including a transmission, a drive pinion gear to which power from the transmission is transmitted, a differential ring gear meshing with the drive pinion gear, and a differential gear coupled to the differential ring gear.
- a diff drive pinion gear made of a small diameter helical gear, a diff ring gear made of a large diameter helical gear, and an end face of the diff ring gear are connected to an oil pump.
- a method of injecting and supplying lubricating oil from a nozzle formed in the pipe toward a differential drive pinion gear see, for example, Patent Document 1.
- the tooth width of the differential drive pinion gear is wider than the tooth width of the differential ring gear, and from the nozzle of the pipe toward the meshing start tooth end that starts meshing with the differential ring gear of the differential drive pinion gear. Lubricating oil is injected.
- the lubricating oil supplied to the said tooth end is supplied to the whole tooth surface along the tooth surface which meshes sequentially.
- the differential drive pinion gear includes Even if the lubricating oil is supplied toward the tooth edge at the beginning of meshing, the differential drive pinion gear may not be sufficiently cooled.
- the amount of working fluid supplied to the meshing portion of the drive pinion gear and the diff ring gear depends on the rotational speed of the diff ring gear and the amount of working fluid accumulated at the bottom of the case.
- the main object of the present invention is to better cool the drive pinion gear meshing with the diff ring gear, and to further improve the durability of the drive pinion gear.
- the power transmission device employs the following means in order to achieve the main object.
- the power transmission device includes: In a power transmission device mounted on a vehicle, including a transmission, a drive pinion gear to which power from the transmission is transmitted, a differential ring gear meshing with the drive pinion gear, and a differential gear coupled to the differential ring gear , A coolant supply pipe configured to supply a cooling medium toward the drive pinion gear on the exit side of the meshing portion when the vehicle travels forward from the meshing portion of the drive pinion gear and the diff ring gear; It is characterized by.
- This power transmission device is configured to supply a cooling medium toward the drive pinion gear on the exit side (meshing end side) of the meshing portion when the vehicle travels forward from the meshing portion of the drive pinion gear and the diff ring gear.
- a refrigerant supply pipe is provided.
- the cooling medium is supplied from the refrigerant supply pipe to the tooth surface of the tooth of the drive pinion gear after meshing whose temperature has risen due to the tooth surface slippage at the meshing portion with the diff ring gear, so that the drive pinion gear can be cooled better. It becomes possible. As a result, it is possible to better suppress the occurrence of pitching of the drive pinion gear caused by the reduction in the tooth surface hardness due to the temper softening effect.
- the “exit side of the meshing portion when the vehicle travels forward” refers to an area until the teeth of the drive pinion gear that meshes with the diff ring gear rotate 180 ° in the rotational direction during forward travel of the vehicle.
- the refrigerant supply pipe may include a refrigerant outlet having a refrigerant outlet that blows out a cooling medium toward the drive pinion gear, and the drive pinion gear has the power transmission device mounted on the vehicle.
- the refrigerant supply pipe may be disposed above the diff ring gear, and the refrigerant supply pipe may be disposed such that the refrigerant blowing portion extends below the drive pinion gear in a state where the power transmission device is mounted on the vehicle.
- a cooling medium may be supplied from the refrigerant blowing portion to the drive pinion gear from below to above.
- the refrigerant blowout part of the refrigerant supply pipe can be arranged in an excess space formed between the drive pinion gear and the diffring gear below the drive pinion gear that is generally smaller in diameter than the diffring gear. It is possible to effectively suppress the enlargement of the power transmission device associated with the installation of the refrigerant supply pipe by effectively using the surplus space. Then, by supplying the cooling medium from the refrigerant blowing part to the drive pinion gear from the lower side to the upper side, compared to the case where the cooling medium is blown from the upper side to the drive pinion gear, bubbling of the cooling medium due to gear agitation and the drive pinion gear It is possible to suppress the retention of bubbles in the vicinity very well.
- the drive pinion gear and the diff ring gear may be helical gears
- the refrigerant supply pipe includes a refrigerant blow-out portion having two refrigerant blow-out openings for blowing a cooling medium toward the drive pinion gear.
- one of the two refrigerant outlets may be formed in the refrigerant outlet so as to be positioned on one end face side of the drive pinion gear with respect to the center in the tooth width direction of the drive pinion gear.
- the other refrigerant outlet may be formed in the refrigerant outlet so as to be located on the other end face side of the drive pinion gear from the center in the tooth width direction of the drive pinion gear.
- the meshing portion between the drive pinion gear teeth and the diff ring gear teeth is rotated from the end surface side of one of the drive pinion gears to the other end surface. Move to the side. Then, in the region on the one end surface side where the engagement of the teeth of the drive pinion gear and the teeth of the diff ring gear starts, the surface pressure at the meshing portion increases, and in the region on the other end surface side where the meshing of both ends is completed. The oil film is broken and pitching is likely to occur.
- the refrigerant supply pipe is configured such that the refrigerant blowing portion is separated from the shaft center of the drive pinion gear than the tooth tip of the drive pinion gear, and is separated from the shaft center of the diff ring gear than the tooth tip of the diff ring gear. May be arranged. Accordingly, at least a part of the refrigerant blowing portion can be disposed so as to face the drive pinion gear on the inner side of both end surfaces in the axial direction of the drive pinion gear and on the outlet side with respect to the meshing portion with the differential ring gear. As a result, it is possible to sufficiently supply the cooling medium from the refrigerant outlet of the refrigerant outlet to the drive pinion gear to cool the drive pinion gear even better.
- the refrigerant outlet may be formed in the refrigerant outlet so as to blow out the cooling medium toward the axis of the drive pinion gear.
- the refrigerant supply pipe may be arranged such that the refrigerant blowing portion extends along the axial direction of the drive pinion gear.
- the refrigerant blowing portion extends along the axial direction of the drive pinion gear.
- FIG. 2 is an operation table showing a relationship between each shift stage of an automatic transmission included in the power transmission device of FIG. 1 and operation states of clutches and brakes. It is a front view which shows the principal part of the power transmission device of FIG. It is a perspective view which shows the principal part of the power transmission device of FIG. It is a top view which shows the principal part of the power transmission device of FIG.
- FIG. 1 is a schematic configuration diagram of a power transmission device 20 according to an embodiment of the present invention.
- a power transmission device 20 shown in the figure is connected to a crankshaft of an engine (not shown) mounted on a front wheel drive vehicle and can transmit power from the engine to left and right drive wheels (front wheels) (not shown).
- the power transmission device 20 includes a converter case 221, a transmission case 22 including a transaxle case 222 coupled to the converter housing 221, and a fluid transmission device (starting device) 23 accommodated in the converter housing 221.
- the fluid transmission device 23 includes an input-side pump impeller 23p connected to an engine crankshaft, an output-side turbine runner 23t, a pump impeller 23p, and a turbine runner 23t connected to an input shaft 31 of the automatic transmission 30. And a torque converter having a stator 23s that rectifies the flow of hydraulic oil from the turbine runner 23t to the pump impeller 23p, a one-way clutch 23o that restricts the rotational direction of the stator 23s in one direction, a lock-up clutch 23c, and the like.
- the fluid transmission device 23 may be configured as a fluid coupling that does not have the stator 23s.
- the oil pump 24 includes a pump assembly including a pump body and a pump cover, an external gear connected to the pump impeller 23p of the fluid transmission device 23 via a hub, an internal gear that meshes with the external gear, and the like. It is configured as.
- the oil pump 24 is driven by the power from the engine and draws hydraulic oil (ATF) stored in an oil pan (not shown) to generate the hydraulic pressure required by the fluid transmission device 23 and the automatic transmission 30 (not shown). Pump to hydraulic control device.
- ATF hydraulic oil
- the automatic transmission 30 is configured as a four-speed transmission, and, as shown in FIG. 2, a Ravigneaux planetary gear mechanism 32 and a plurality of power transmission paths for changing the power transmission path from the input side to the output side. Clutches C1, C2 and C3, two brakes B1 and B3, and a one-way clutch F2.
- the Ravigneaux type planetary gear mechanism 32 includes a first sun gear 33a and a second sun gear 33b which are external gears, a ring gear 34 which is an internal gear disposed concentrically with the first and second sun gears 33a and 33b, A plurality of short pinion gears 35a meshing with one sun gear 33a, a plurality of long pinion gears 35b meshing with the second sun gear 33b and the plurality of short pinion gears 35a and meshing with the ring gear 34, a plurality of short pinion gears 35a and a plurality of long pinion gears 35b And a planetary carrier 36 that holds the motor in a rotatable (rotatable) and revolving manner.
- the ring gear 34 of the Ravigneaux planetary gear mechanism 32 functions as an output member of the automatic transmission 30, and the power transmitted from the input shaft 31 to the ring gear 34 is transmitted to the left and right drive wheels via the gear mechanism 40 and the differential gear 50. Communicated.
- the planetary carrier 36 is supported by the transmission case 22 via the one-way clutch F2, and the rotation direction of the planetary carrier 36 is limited to one direction by the one-way clutch F2.
- the clutch C1 has a hydraulic servo composed of a piston, a plurality of friction plates and mating plates, an oil chamber to which hydraulic oil is supplied, and the like, and includes an input shaft 31 and a first sun gear 33a of the Ravigneaux type planetary gear mechanism 32.
- the hydraulic clutch can be connected to each other and can be disconnected.
- the clutch C2 has a hydraulic servo composed of a piston, a plurality of friction plates and mating plates, an oil chamber to which hydraulic oil is supplied, and the like.
- the input shaft 31 and the planetary carrier 36 of the Ravigneaux planetary gear mechanism 32 are connected to each other. This is a hydraulic clutch that can be connected and released from both.
- the clutch C3 has a hydraulic servo composed of a piston, a plurality of friction plates, a counter plate, an oil chamber to which hydraulic oil is supplied, and the like, and includes an input shaft 31 and a second sun gear 33b of the Ravigneaux planetary gear mechanism 32.
- the hydraulic clutch can be connected to each other and can be disconnected.
- the brake B1 is configured as a band brake including a hydraulic servo or a multi-plate friction brake, and fixes the second sun gear 33b of the Ravigneaux type planetary gear mechanism 32 to the transmission case 22 and also fixes the second sun gear 33b to the transmission case 22.
- This is a hydraulic clutch that can be released.
- the brake B3 is configured as a band brake including a hydraulic servo or a multi-plate friction brake, and fixes the planetary carrier 36 of the Ravigneaux planetary gear mechanism 32 to the transmission case 22 and also fixes the planetary carrier 36 to the transmission case 22. It is a hydraulic clutch that can be released.
- FIG. 2 shows an operation table showing the relationship between the respective shift stages of the automatic transmission 30 and the operating states of the clutches C1 to C3, the brakes B1 and B3, and the one-way clutch F2.
- the automatic transmission 30 provides the first to fourth forward speeds and the first reverse speed by setting the clutches C1 to C3 and the brakes B1 and B3 to the states shown in the operation table of FIG.
- at least one of the clutches C1 to C3 and the brakes B1 and B3 may be a meshing engagement element such as a dog clutch.
- the gear mechanism 40 is fixed to a counter drive gear 41 connected to the ring gear 34 of the Ravigneaux planetary gear mechanism 32 of the automatic transmission 30 and a counter shaft 42 extending in parallel with the input shaft 31 of the automatic transmission 30.
- a counter driven gear 43 meshed with the counter drive gear 41, a drive pinion gear (final drive gear) 44 formed (or fixed) on the counter shaft 42, and a diff ring gear (final driven gear) 45 meshed with the drive pinion gear 44.
- the drive pinion gear 44 is formed with a smaller diameter than the diff ring gear 45 and is disposed above the diff ring gear 45 in the transmission case 22 when the power transmission device 20 is mounted on the vehicle.
- the diff ring gear 45 is connected to the differential gear 50.
- the drive pinion gear 44 and the diff ring gear 45 are configured as helical gears.
- FIGS. show the configuration around the drive pinion gear 44 and the diff ring gear 45 of the power transmission device 20. 3 to 5, the lower side in the figure indicates the lower side in the vertical direction.
- the power transmission device 20 includes a refrigerant supply pipe 60 that supplies hydraulic oil as a cooling medium to the drive pinion gear 44.
- the refrigerant supply pipe 60 extends from the refrigerant outlet 61 and has a plurality of (two in this embodiment) refrigerant outlets 61o for blowing out the hydraulic oil toward the drive pinion gear 44, and the converter housing.
- the refrigerant inflow portion 62 connected to the oil hole 221a formed in the 221 and the refrigerant blowout portion 61 extend from the periphery of the differential gear 50 (see the rough broken line in FIG. 3) and are formed in the converter housing 221.
- a refrigerant outflow portion 63 connected to the oil hole 221b.
- the oil hole 221a to which the refrigerant inflow portion 62 is connected is connected to an oil passage (both not shown) of the hydraulic control device via an oil passage formed in the converter housing 221.
- the oil hole 221b to which the refrigerant outflow portion 63 is connected is connected to an oil passage (both not shown) that is formed in the converter housing 221 and opens in the vicinity of the bearing that supports the differential gear 50. .
- the refrigerant outlet 61 is separated from the axis 44 o of the drive pinion gear 44 than the tooth tip of the drive pinion gear 44 (see the fine broken line in FIG. 3), and the tooth tip of the diff ring gear 45 (in FIG. 3) It is arranged in the transmission case 22 so as to be further away from the shaft center 45o of the differential ring gear 45 than the two-dot chain line).
- the refrigerant blowing portion 61 can be opposed to the drive pinion gear 44 inside the both end surfaces 44 a and 44 b in the axial direction of the drive pinion gear 44.
- the refrigerant supply pipe 60 is configured such that, in a state where the power transmission device 20 is mounted on the vehicle, the refrigerant outlet 61 is below the drive pinion gear 44 having a smaller diameter than the diff ring gear 45, and the drive pinion gear 44. Is arranged so as to extend substantially along the axial direction of the drive pinion gear 44 with a surplus space formed between the drive pinion gear 44 and the differential ring gear 45.
- the refrigerant blowing portion 61 of the refrigerant supply pipe 60 in the surplus space formed between the drive pinion gear 44 and the diff ring gear 45, the surplus space is effectively used to install the refrigerant supply pipe 60. Therefore, it is possible to satisfactorily suppress the increase in size of the power transmission device 20 associated with.
- the drive pinion gear 44 rotates in the forward direction (clockwise in the figure) indicated by the broken line arrows in FIGS. 3 and 4. ). Therefore, by disposing the refrigerant supply pipe 60 in the transmission case 22 as described above, the refrigerant blowing portion 61 is located downstream in the forward rotation direction from the meshing portion between the drive pinion gear 44 and the diffring gear 45, that is, the vehicle. Is opposed to the drive pinion gear 44 on the exit side of the meshing portion when traveling forward (the traveling side in the rotational direction of the drive pinion gear 44).
- the “downstream side”, that is, “the exit side of the meshing part when the vehicle travels forward (meshing end side)” is the axis of the drive pinion gear 44, the meshing part of the drive pinion gear 44 and the diff ring gear 45, and the diff ring gear 45.
- the region below the straight line passing through the shaft center and below the drive pinion gear 44 is shown.
- the “downstream side” is a region above the straight line and above the drive pinion gear 44. Indicates.
- the “downstream side” refers to an area until the teeth of the drive pinion gear 44 that meshes with the diff ring gear 45 rotate 180 ° in the forward rotation direction of the drive pinion gear 44.
- refrigerant blowing portion 61 is preferably below the straight line orthogonal to the straight line and below drive pinion gear 44. It is preferable to arrange on the lower side.
- the refrigerant outlet 61 is connected to the refrigerant inflow portion 62 and extends substantially along the axial direction of the drive pinion gear 44.
- An upper pipe portion 612 that is connected to the refrigerant outflow portion 63 and extends at a slight angle in the vertical direction with respect to the axial direction of the drive pinion gear 44 below and in the vicinity of the drive pinion gear 44, and a lower pipe portion 611 And a curved portion 613 extending between the upper tube portion 612. That is, in the present embodiment, a part of the upper pipe portion 612 of the refrigerant blowing portion 61 faces the drive pinion gear 44 on the inner side of both end surfaces 44a and 44b in the axial direction of the drive pinion gear 44.
- the plurality of refrigerant outlets 61o are formed at the upper portion of the refrigerant outlet 61 so as to open upward and to blow out the hydraulic oil toward the axis of the drive pinion gear 44 (from below to above). . That is, as shown in FIGS. 3 to 5, the plurality of refrigerant outlets 61 o are provided on the outer peripheral surface on the upper side of the upper pipe portion 612 of the refrigerant outlet 61 from both end surfaces 44 a and 44 b in the axial direction of the drive pinion gear 44. Are formed at predetermined intervals substantially along the axial direction so as to be located inside.
- the hydraulic oil is blown out from the plurality of refrigerant outlets 61o toward the tooth surfaces of the teeth of the drive pinion gear 44 on the downstream side in the forward rotation direction from the meshing portion of the drive pinion gear 44 and the diff ring gear 45.
- the curved portion 613 is formed at a position slightly protruding in the axial direction of the diffring gear 45 from the end surface 45a of the diffring gear 45 opposite to the converter housing 221.
- the curved portion 613 may be formed closer to the converter housing 221 than the end surface of the diff ring gear 45.
- the hydraulic oil supplied to the refrigerant inflow portion 62 further flows into the refrigerant blowout portion 61, and a plurality of refrigerant blowout ports 61 o that are partly formed on the outer peripheral surface of the upper pipe portion 612 of the refrigerant blowout portion 61. Then, the air is blown toward the drive pinion gear 44 on the downstream side in the forward rotation direction of the drive pinion gear 44 from the meshing portion of the drive pinion gear 44 and the diff ring gear 45 (see solid line arrows shown in FIGS. 3 to 5).
- the working oil as the cooling medium is supplied from the refrigerant supply pipe 60 to the tooth surfaces of the meshed drive pinion gear 44 whose temperature has risen due to the tooth surface slippage at the meshing portion with the differential ring gear 45, and the drive pinion gear 44. Can be cooled better.
- the drive pinion gear that is formed with a smaller diameter than the diff ring gear 45 and that suppresses the temperature rise of the drive pinion gear that is easily affected by heat, and the tooth surface hardness decreases due to the temper softening effect. It becomes possible to suppress generation
- the plurality of refrigerant outlets 61o are located on the inner side of the both end surfaces 44a and 44b in the axial direction of the drive pinion gear 44 and below the drive pinion gear 44, and the shaft of the drive pinion gear 44 is arranged. Arranged generally along the direction. As a result, hydraulic oil can be supplied evenly from the plurality of refrigerant outlets 61o to the entire tooth surface of the drive pinion gear 44, and the drive pinion gear 44 can be cooled extremely well. Therefore, in the power transmission device 20, the durability of the drive pinion gear 44 can be further improved.
- one of the two refrigerant outlets 61o of the refrigerant outlet 61 is located closer to the end surface 44a side of one of the drive pinion gears 44 (the vehicle rear side) than the center in the tooth width direction of the drive pinion gear 44.
- the other of the two refrigerant outlets 61o is positioned closer to the end face 44b side of the other side (vehicle front side) of the drive pinion gear 44 than the center in the tooth width direction of the drive pinion gear 44. It forms in the refrigerant
- one of the two refrigerant outlets 61o of the refrigerant outlet 61 is arranged so as to be located on the one end face 44a side of the drive pinion gear, and the other is arranged so as to be located on the other end face 44b side of the drive pinion gear 44.
- the drive pinion gear 44 that meshes with the differential ring gear 45 can be cooled extremely well, and the durability of the drive pinion gear 44 can be further improved.
- the hydraulic oil that has passed through the refrigerant blow-out part 61 flows into the oil hole 221b of the converter housing 221 through the refrigerant outflow part 63, and to a bearing (not shown) that supports the differential gear 50 through an oil path (not shown). Supplied. As a result, the bearing supporting the differential gear 50 can also be lubricated and cooled.
- the hydraulic oil supplied to a bearing (not shown) that supports the drive pinion gear 44 and the differential gear 50 flows into a hydraulic oil reservoir (not shown) and is pumped again to the hydraulic control device by the oil pump 24.
- the power transmission device 20 operates as a cooling medium toward the drive pinion gear 44 on the downstream side in the forward rotation direction of the drive pinion gear 44 from the meshing portion of the drive pinion gear 44 and the diff ring gear 45.
- a refrigerant supply pipe 60 configured to supply oil is provided.
- hydraulic oil is supplied from the refrigerant supply pipe 60 to the tooth surface of the meshed drive pinion gear 44 whose temperature has increased due to the sliding of the tooth surface at the meshing portion with the diff ring gear 45, and the drive pinion gear 44 is made better.
- the drive pinion gear 44 that meshes with the diffring gear 45 can be cooled better, and the durability of the drive pinion gear 44 can be further improved.
- the refrigerant supply pipe 60 has a refrigerant outlet 61 having a refrigerant outlet 61o for blowing out hydraulic oil toward the drive pinion gear 44, and the refrigerant outlet 61 is closer to the drive pinion gear 44 than the tooth tip of the drive pinion gear 44. It is arranged so as to be separated from the shaft center and further away from the shaft center of the diff ring gear 45 than the tooth tip of the diff ring gear 45.
- at least a part of the refrigerant blowing portion 61 is opposed to the drive pinion gear 44 on the inner side of both end surfaces in the axial direction of the drive pinion gear 44 and on the downstream side of the meshing portion with the diff ring gear 45 in the forward rotation direction. It becomes possible to arrange.
- the cooling medium can be sufficiently supplied from the refrigerant outlet 61o of the refrigerant outlet 61 to the drive pinion gear 44 to cool the drive pinion gear 44 even better.
- the refrigerant supply pipe 60 may be arranged such that the refrigerant blowing portion 61 is closer to the shaft center of the drive pinion gear 44 than the tooth tip of the drive pinion gear 44, and the refrigerant blowing portion 61 is disposed on the teeth of the diffring gear 45. It may be arranged so as to be closer to the axis of the diff ring gear 45 than before.
- the drive pinion gear 44 is disposed above the diff ring gear 45 in a state where the power transmission device 20 is mounted on the vehicle, and the refrigerant supply pipe 60 is a refrigerant blowing portion in a state where the power transmission device 20 is mounted on the vehicle.
- 61 is arranged to extend below drive pinion gear 44.
- the refrigerant outlet 61o is formed in the upper part of the refrigerant outlet 61 so as to open upward, and the coolant is supplied from the refrigerant outlet 61 to the drive pinion gear 44 from below to above.
- the refrigerant outlet 61 of the refrigerant supply pipe 60 is disposed in an excess space formed between the drive pinion gear 44 and the diff ring gear 45 below the drive pinion gear 44, which is generally smaller in diameter than the diff ring gear 45. Therefore, it is possible to effectively suppress the enlargement of the power transmission device 20 associated with the installation of the refrigerant supply pipe 60 by effectively using the surplus space. Then, by supplying the cooling medium from the refrigerant blowing portion 61 to the drive pinion gear 44 from the lower side to the upper side, compared to the case where the cooling medium is blown from the upper side to the drive pinion gear 44, bubbles of the cooling medium due to gear agitation are generated.
- the drive pinion gear 44 may not be disposed above the diff ring gear 45.
- the refrigerant supply pipe 60 has the refrigerant blowing portion 61 extending above the drive pinion gear 44. May be arranged as follows.
- the refrigerant supply pipe 60 is arranged such that the refrigerant outlet 61 extends along the axial direction of the drive pinion gear 44. Accordingly, if a plurality of refrigerant outlets 61o of the refrigerant outlet 61 are formed along the axial direction of the drive pinion gear 44, the teeth of the drive pinion gear 44 after meshing with the teeth of the diff ring gear 45 from the plurality of refrigerant outlets 61o.
- the hydraulic oil can be supplied evenly over the entire tooth surface.
- the drive pinion gear 44 can be cooled extremely well.
- at least one refrigerant outlet 61o may be formed on the outer peripheral surface of the upper pipe portion 612. Further, the refrigerant blowing part 61 does not necessarily have to extend along the axial direction of the drive pinion gear 44.
- the automatic transmission 30, the drive pinion gear 44 to which the power from the automatic transmission 30 is transmitted, the differential ring gear 45 meshing with the drive pinion gear 44, and the differential gear coupled to the differential ring gear 45 are provided.
- 50 is equivalent to the “power transmission device”, and the hydraulic oil is directed toward the drive pinion gear 44 on the downstream side in the forward rotation direction of the drive pinion gear 44 from the meshing portion of the drive pinion gear 44 and the diff ring gear 45.
- the refrigerant supply pipe 60 configured to supply the refrigerant corresponds to the “refrigerant supply pipe”, and the refrigerant outlet 61 having the refrigerant outlet 61o for blowing the hydraulic oil toward the drive pinion gear 44 corresponds to the “refrigerant outlet”. To do.
- the present invention can be used in the power transmission device manufacturing industry and the like.
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Abstract
Description
変速機と、該変速機からの動力が伝達されるドライブピニオンギヤと、該ドライブピニオンギヤに噛合するデフリングギヤと、該デフリングギヤに連結されるデファレンシャルギヤとを含み、車両に搭載される動力伝達装置において、
前記ドライブピニオンギヤと前記デフリングギヤとの噛合部よりも前記車両が前進走行するときの前記噛合部の出口側で前記ドライブピニオンギヤに向けて冷却媒体を供給するように構成された冷媒供給管を備えることを特徴とする。
Claims (6)
- 変速機と、該変速機からの動力が伝達されるドライブピニオンギヤと、該ドライブピニオンギヤに噛合するデフリングギヤと、該デフリングギヤに連結されるデファレンシャルギヤとを含み、車両に搭載される動力伝達装置において、
前記ドライブピニオンギヤと前記デフリングギヤとの噛合部よりも前記車両が前進走行するときの前記噛合部の出口側で前記ドライブピニオンギヤに向けて冷却媒体を供給するように構成された冷媒供給管を備えることを特徴とする動力伝達装置。 - 請求項1に記載の動力伝達装置において、
前記冷媒供給管は、前記ドライブピニオンギヤに向けて冷却媒体を吹き出す冷媒吹出口を有する冷媒吹出部を含み、
前記ドライブピニオンギヤは、前記動力伝達装置が前記車両に搭載された状態において前記デフリングギヤよりも上方に配置され、
前記冷媒供給管は、前記動力伝達装置が前記車両に搭載された状態において前記冷媒吹出部が前記ドライブピニオンギヤの下方に延在するように配置され、下方から上方に向けて、前記冷媒吹出部から前記ドライブピニオンギヤに冷却媒体を供給することを特徴とする動力伝達装置。 - 請求項1または2に記載の動力伝達装置において、
前記ドライブピニオンギヤおよび前記デフリングギヤは、はすば歯車であり、
前記冷媒供給管は、それぞれ前記ドライブピニオンギヤに向けて冷却媒体を吹き出す2つの冷媒吹出口を有する冷媒吹出部を含み、
前記2つの冷媒吹出口の一方は、前記ドライブピニオンギヤの歯幅方向における中心よりも該ドライブピニオンギヤの一方の端面側に位置するように前記冷媒吹出部に形成され、前記2つの冷媒吹出口の他方は、前記ドライブピニオンギヤの歯幅方向における中心よりも該ドライブピニオンギヤの他方の端面側に位置するように前記冷媒吹出部に形成されることを特徴とする動力伝達装置。 - 請求項3に記載の動力伝達装置において、
前記冷媒供給管は、前記冷媒吹出部が前記ドライブピニオンギヤの歯先よりも該ドライブピニオンギヤの軸心から離間すると共に、前記デフリングギヤの歯先よりも該デフリングギヤの軸心から離間するように配置されることを特徴とする動力伝達装置。 - 請求項2から4の何れか一項に記載の動力伝達装置において、
前記冷媒吹出口は、前記ドライブピニオンギヤの軸心に向けて前記冷却媒体を吹き出すように前記冷媒吹出部に形成されることを特徴とする動力伝達装置。 - 請求項2から5の何れか一項に記載の動力伝達装置において、
前記冷媒供給管は、前記冷媒吹出部が前記ドライブピニオンギヤの軸方向に沿って延在するように配置されることを特徴とする動力伝達装置。
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JP2009156368A (ja) * | 2007-12-27 | 2009-07-16 | Aisin Aw Co Ltd | 歯車回転伝達装置 |
JP2010090979A (ja) * | 2008-10-07 | 2010-04-22 | Aisin Aw Co Ltd | 車両用動力伝達装置 |
JP2010242900A (ja) * | 2009-04-08 | 2010-10-28 | Toyota Motor Corp | 車両駆動装置の発熱部冷却構造 |
WO2012028231A1 (de) * | 2010-09-02 | 2012-03-08 | Voith Patent Gmbh | Zahnradgetriebe |
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JPH11337449A (ja) * | 1998-05-27 | 1999-12-10 | Hitachi Ltd | 歯車装置 |
JP4665434B2 (ja) * | 2004-05-14 | 2011-04-06 | トヨタ自動車株式会社 | 歯車機構の潤滑装置 |
JP5011052B2 (ja) * | 2007-10-03 | 2012-08-29 | 株式会社日立ニコトランスミッション | 歯車装置 |
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JP2009156368A (ja) * | 2007-12-27 | 2009-07-16 | Aisin Aw Co Ltd | 歯車回転伝達装置 |
JP2010090979A (ja) * | 2008-10-07 | 2010-04-22 | Aisin Aw Co Ltd | 車両用動力伝達装置 |
JP2010242900A (ja) * | 2009-04-08 | 2010-10-28 | Toyota Motor Corp | 車両駆動装置の発熱部冷却構造 |
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