WO2014054490A1 - 駆動力伝達装置の潤滑構造 - Google Patents
駆動力伝達装置の潤滑構造 Download PDFInfo
- Publication number
- WO2014054490A1 WO2014054490A1 PCT/JP2013/075957 JP2013075957W WO2014054490A1 WO 2014054490 A1 WO2014054490 A1 WO 2014054490A1 JP 2013075957 W JP2013075957 W JP 2013075957W WO 2014054490 A1 WO2014054490 A1 WO 2014054490A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- planetary gear
- lubricating oil
- oil
- oil passage
- guide member
- Prior art date
Links
- 238000005461 lubrication Methods 0.000 title claims abstract description 63
- 230000005540 biological transmission Effects 0.000 title claims description 22
- 230000002093 peripheral effect Effects 0.000 claims abstract description 16
- 239000003921 oil Substances 0.000 claims description 89
- 239000010687 lubricating oil Substances 0.000 claims description 56
- 230000001050 lubricating effect Effects 0.000 claims description 16
- 239000000314 lubricant Substances 0.000 claims description 6
- 238000010586 diagram Methods 0.000 description 5
- 230000006866 deterioration Effects 0.000 description 3
- 239000002783 friction material Substances 0.000 description 3
- 238000003780 insertion Methods 0.000 description 3
- 230000037431 insertion Effects 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
Images
Classifications
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
- F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
-
- 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
- F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/74—Features relating to 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
- F16H57/0473—Friction devices, e.g. clutches or brakes
-
- 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
- F16H57/0479—Gears or bearings on planet carriers
-
- 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
-
- 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
- F16H57/0484—Gearings with gears having orbital motion with variable gear ratio or for reversing rotary motion
-
- 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
Definitions
- the present invention relates to a lubrication structure for lubricating a planetary gear (planetary gear mechanism) and an engagement element constituting a driving force transmission device in a driving force transmission device for transmitting a driving force from a driving source.
- An automatic transmission (driving force transmission device) provided in an automobile includes a speed change mechanism including a planetary gear (planetary gear mechanism) as a speed change mechanism for shifting and outputting a driving force from an input shaft (rotary shaft).
- the planetary gear includes a sun gear installed on the input shaft, a carrier that supports a plurality of pinion gears and a pinion shaft on the outer diameter side of the sun gear, and a ring gear that meshes with the pinion gear on the outer diameter side of the carrier.
- an oil catch plate lubricating oil guide member for guiding lubricating oil to an end portion (end portion in the axial direction) of the carrier is attached. is there.
- the oil catch plate supplies lubricating oil to a rotating sliding contact portion such as a bearing provided between the pinion shaft and the pinion gear.
- an engagement element such as a clutch or a brake is arranged on the outer diameter side of the planetary gear installed on the input shaft so as to overlap each other in the radial direction.
- a part of the lubricating oil supplied from the input shaft side is captured by the oil catch plate and supplied into the planetary gear.
- the remaining lubricating oil passes through the outside of the oil catch plate and is supplied to engaging elements such as a clutch and a brake.
- Patent Document 3 discloses an oil catch plate configured to optimize the ratio of the lubricating oil supplied to the planetary gear and the ratio of the lubricating oil supplied to the engagement element in such a lubricating structure. Has been.
- the ratio of the amount of lubrication (amount of lubricating oil) required by the planetary gears and the lubrication required by the engagement elements There is a change (difference) in the proportion of quantity. For example, the ratio of the amount of lubrication required by the engagement element increases as the number of rotations of the rotating shaft increases, but the ratio of the amount of lubrication required by the planetary gear does not increase as much as the number of rotations increases. .
- the present invention has been made in view of the above problems, and even when the ratio of the required lubrication amount of each part changes due to a change in the rotational speed, the lubrication amount for each part is appropriately adjusted according to the change. It is an object of the present invention to provide a lubrication structure for a driving force transmission device that can be used.
- the present invention is as follows.
- a lubrication structure for a driving force transmission device includes a planetary gear (1) having a plurality of rotating elements (10, 30, 40) arranged in a predetermined relationship around a rotating shaft (2), and the planetary gear.
- An engaging element (80) disposed on the outer peripheral side of (1) and a lubricating oil guide member (60) for guiding the lubricating oil attached to the planetary gear (1).
- the first oil passage (64, 62) for guiding the lubricating oil supplied from the rotating shaft (2) side into the planetary gear (1) and the lubricating oil supplied from the rotating shaft (2) side.
- the opening / closing means (70) is configured such that the valve body (72) is seated on the valve seat portion (71) by the urging force of the urging means (73).
- 3 is an on-off valve that closes the oil passage (65), and the valve body (72) is urged by the urging means (73) by the centrifugal force applied to the valve body (72) by the rotation of the lubricating oil guide member (60).
- the valve seat portion (71) may be separated from the biasing force. According to this, with a simple configuration, the on-off valve can be automatically opened according to the number of rotations of the rotating shaft, and the distribution of the lubrication amount between the planetary gear and the engagement element can be adjusted appropriately.
- the lubricant guide member (60) is a member formed in a circular annular flat plate shape, and the first oil passages (64, 62) are the lubricant guide. It includes a groove (64) that is formed on the inner diameter side of the member (60) and is recessed toward the outer diameter side, and the third oil passage (65) extends from the groove (64) to the outer peripheral edge of the lubricating oil guide member (60) ( 61c) may be a communicating path. According to this, it is possible to appropriately adjust the distribution of the lubrication amount between the engagement element and the planetary gear with a simple configuration.
- the first oil passage (64, 62) includes a cylindrical passage (62) extending from the groove (64) through the lubricating oil guide member (60) to the planetary gear (1) side, and the planetary gear (1 ) Is a sun gear (10) installed on the rotating shaft (2), a carrier (20) that supports a plurality of pinion gears (30) and a pinion shaft (40) on the outer diameter side of the sun gear (10), A ring gear (51) meshing with the pinion gear (30) on the outer diameter side of the carrier (20), and the cylindrical passage (62) receives the lubricating oil supplied from the rotating shaft (2) side with the pinion shaft ( 40) may be guided to the rotational sliding contact portion (32) of the pinion gear (30). According to this configuration, it is possible to optimize the amount of lubrication at the rotational sliding contact portion between the pinion gear and the pinion shaft, which is a portion of the planetary gear that requires lubrication.
- FIG. 3A is a diagram for explaining the operation of the on-off valve.
- FIG. 3A is a diagram showing a state in which the on-off valve is closed
- FIG. 3B is a diagram showing a state in which the on-off valve is opened.
- FIG. 1 is a side sectional view showing a configuration example of a driving force transmission device according to an embodiment of the present invention.
- FIG. 2 is a partially enlarged sectional view of the oil catch plate and its periphery in the driving force transmission device.
- a planetary gear 1 shown in FIG. 1 is a planetary gear that constitutes a gear mechanism for shifting provided in an automatic transmission.
- the planetary gear 1 includes a sun gear 10 that is installed on the input shaft 2 and has outer teeth formed on the outer periphery thereof, a plurality of (for example, five) pinion gears 30 that mesh with the outer teeth of the sun gear 10, and a plurality of pinion gears 30.
- a carrier 20 to be supported and a rotating member 50 installed on the outer peripheral side of the carrier 20 are provided.
- a ring gear 51 that meshes with the pinion gear 30 is formed on the inner periphery of the rotating member 50.
- the axial direction refers to the axial direction of the input shaft 2.
- a circular annular oil catch plate (lubricating oil guide member) 60 is attached to one end of the carrier 20 in the axial direction.
- a clutch or brake (hereinafter referred to as “engagement element”) 80 provided between the casing 85, which is a fixed member, and the rotating member 50 is disposed.
- the engagement element 80 is a friction engagement type engagement in which a plurality of friction materials 81a attached to the casing 85 side and other friction materials 81b attached to the rotating member 50 side are alternately stacked along the axial direction.
- the rotating member 50 is locked to the casing 85 by pressing the laminated friction materials 81a and 81b in the axial direction.
- the engagement element 80 is a wet friction engagement element to which lubricating oil is supplied from the input shaft 2 side.
- the input shaft (rotating shaft) 2 is rotated by a driving force from a driving source such as an engine.
- the input shaft 2 is formed with a hollow shaft oil passage 3 extending in the axial direction inside the input shaft 2 and a radial oil passage 4 penetrating from the shaft oil passage 3 outward in the radial direction.
- Lubricating oil introduced into the shaft oil passage 3 of the input shaft 2 passes through the shaft oil passage 3, passes through the radial oil passage 4, and is discharged from the opening 4 a of the radial oil passage 4 that opens to the outer peripheral side surface of the input shaft 2. Is done.
- the sun gear 10 of the planetary gear 1 is splined to the outer periphery of the input shaft 2.
- the carrier 20 includes a circular annular main body portion 25 that is rotatably installed around the input shaft 2, and a small-diameter cylindrical flange portion 26 that is integrally formed on the inner peripheral side of the main body portion 25.
- the input shaft 2 is disposed on the inner diameter side of the flange portion 26.
- a guide hole 20 a for guiding the lubricating oil discharged from the radial oil passage 4 to the oil catch plate 60 side is formed at a position corresponding to the radial oil passage 4 of the input shaft 2 in the carrier 20. .
- a pinion shaft 40 is installed in the shaft hole 20b provided in the carrier 20, a pinion shaft 40 is installed.
- the pinion shaft 40 is supported in parallel to the input shaft 2 on the outer peripheral side of the input shaft 2.
- a pinion gear 30 is pivotally supported on the pinion shaft 40 via a bearing 32.
- a washer (thrust washer) 31 that receives an axial load is attached to both ends of the pinion gear 30 supported by the pinion shaft 40 in the axial direction.
- a plurality of sets (for example, 5 sets) of the pinion shaft 40 and the pinion gear 30 are installed at equal intervals along the circumferential direction of the carrier 20.
- a hollow portion 45 formed of an elongated hole extending in the axial direction is formed inside the pinion shaft 40. The hollow portion 45 opens at one end portion (end portion on the oil catch plate 60 side) in the axial direction of the pinion shaft 40.
- the oil catch plate 60 is a cylinder composed of a circular flat plate-shaped main body portion 61 having a through hole at the center and a small cylindrical protrusion provided on the side surface 61 a of the main body portion 61 on the carrier 20 side.
- the unit 62 is integrally provided.
- the cylindrical part 62 protrudes perpendicularly from the side surface 61 a of the main body part 61, and a plurality (for example, five) are formed at equal intervals along the circumferential direction of the main body part 61.
- a hollow portion 62 a made up of a hollow through hole is formed inside the cylindrical portion 62.
- a substantially flat collar portion 63 extending inward in the radial direction is formed on the inner diameter side of the main body portion 61 so as to protrude, and the guide hole 20a of the carrier 20 is formed on the side surface 61a side of the collar portion 63.
- a lubricating groove 64 for taking in the lubricating oil released from the is formed.
- the lubrication groove 64 is formed of a bottomed recess having a bottom surface 64 a on the outer side in the radial direction on the inner periphery of the main body 61.
- the hollow portion 62 a of the cylindrical portion 62 communicates with the inner side surface (side surface on the planetary gear 1 side) 64 b of the lubricating groove 64. As shown in FIG.
- the lubricating groove 64 is disposed at a position facing the guide hole 20 a of the carrier 20.
- tip) 63a of the collar part 63 inclines in the direction which leaves
- the opening on the inner diameter side of the lubrication groove 64 facing the guide hole 20a of the carrier 20 is larger than the outer diameter side (the bottom surface 64a side).
- the on-off valve 70 is installed. As shown in FIG. 2, the on-off valve 70 includes a stepped valve seat 71 formed on the outer peripheral surface of the passage 65, a spherical valve body 72 seated on the valve seat 71, and the valve body 72 as a valve. And a coil spring (biasing means) 73 that urges toward the seat portion 71.
- the coil spring 73 is disposed so as to seat the valve body 72 on the valve seat portion 71 by urging the valve body 72 toward the inner side in the radial direction.
- FIG. 3 is a diagram for explaining the operation of the on-off valve 70.
- FIG. 3A is a view showing a state in which the on-off valve 70 is closed
- FIG. 3B is a view showing a state in which the on-off valve 70 is opened.
- the on-off valve 70 has the valve spring 72 attached to the coil spring 73 until the rotational speed of the oil catch plate 60 exceeds a predetermined rotational speed (the rotational speed R1 shown in FIG. 5). It is pressed inward in the radial direction by the force and is seated on the valve seat 71. As a result, the passage 65 is closed by the valve body 72.
- a predetermined rotational speed the rotational speed R1 shown in FIG. 5
- the centrifugal force applied to the valve body 72 along with the rotation of the oil catch plate 60 causes the valve body 72 to move in the radial direction. Move outward (upward in FIG. 2). Thereby, the valve body 72 is separated from the valve seat portion 71 and the passage 65 is opened. Therefore, the lubrication groove 64 of the oil catch plate 60 and the outer peripheral edge 61 c of the main body 61 communicate with each other.
- the on-off valve 70 is configured to open the passage 65 by centrifugal force accompanying the rotation of the oil catch plate 60.
- the oil catch plate 60 having the above configuration is attached to the end portion of the carrier 20 by fastening screws 68.
- the end of the pinion shaft 40 is covered with an oil catch plate 60.
- the cylindrical portion 62 of the oil catch plate 60 is inserted into the hollow portion 45 of the pinion shaft 40.
- the oil catch plate 60 rotates integrally with the carrier 20 as the carrier 20 rotates.
- a pin 75 for preventing the pinion shaft 40 from rotating and preventing the pinion shaft 40 from being inserted is inserted into an end portion of the pinion shaft 40.
- the pin 75 is inserted in the radial direction along the insertion hole 20c provided in the carrier 20 and the insertion hole 40c provided in the pinion shaft 40, and a screw groove and a screw thread provided between the pin 75 and the insertion hole 20c. It is fixed by engagement (screwing).
- FIG. 4 is a diagram showing a path through which the planetary gear 1 and the surrounding lubricating oil flow.
- the flow of the lubricating oil is indicated by a one-dot chain line.
- the on-off valve 70 is closed and the passage 65 is closed.
- the lubricating oil supplied to the shaft oil passage 3 of the input shaft 2 is guided to the radial oil passage 4 by the centrifugal force accompanying the rotation of the input shaft 2.
- Lubricating oil exiting from the radial oil passage 4 is guided to the guide hole 20a of the carrier 20 and discharged (scattered) from the guide hole 20a.
- a part of the lubricating oil discharged from the guide hole 20a is guided to the lubricating groove 64 of the oil catch plate 60 as an oil passage (first oil passage) L1 shown in FIG.
- the lubricating oil guided to the lubricating groove 64 passes through the hollow portion 62 a of the cylindrical portion 62, passes through the hollow portion 45 of the pinion shaft 40 and the through hole 46, and is discharged from the through hole 46.
- the lubricating oil discharged from the through hole 46 is supplied to the bearing 32 interposed between the pinion shaft 40 and the pinion gear 30. Thereby, the bearing 32 is lubricated. Further, a part of the lubricating oil supplied to the bearing 32 is guided to the outer peripheral side of the pinion gear 30 by the centrifugal force accompanying the rotation of the pinion gear 30, and then the engagement element 80 via the ring gear 51 (rotating member 50). Led to.
- the remaining lubricating oil discharged from the guide hole 20a has a diameter along the side surface 61b opposite to the carrier 20 of the oil catch plate 60, as in an oil passage (second oil passage) L2 shown in FIG. Supplied outside the direction.
- the lubricating oil passes through the opening 52 of the rotating member 50 and is guided to the engaging element 80. Thereby, the engagement element 80 is lubricated.
- the on-off valve 70 is opened.
- a passage 65 that connects the lubricating groove 64 of the oil catch plate 60 and the outer peripheral edge 61c is opened. Therefore, in a state where the on-off valve 70 is opened, a part of the lubricating oil guided to the lubricating groove 64 does not go to the hollow portion 62a of the cylindrical portion 62, but the oil passage (third oil passage) shown in FIG. Like L3, it is guided to the engaging element 80 through the passage 65.
- FIG. 5 is a graph showing the relationship between the rotational speed of the oil catch plate 60 (carrier 20) and the flow rate (lubricating amount) of the lubricating oil required for the planetary gear 1 and the engaging element 80.
- the horizontal axis represents the rotational speed R of the oil catch plate 60
- the vertical axis represents the flow rate (lubricating amount) S of the lubricating oil.
- A1 in the graph indicates a target lubrication amount of the engagement element 80 (an optimum lubrication amount in the engagement element 80 that is neither excessively lubricated nor insufficiently lubricated).
- A2 shows the actual amount of lubrication of the engagement element 80 when the oil catch plate 60 is not provided with the on-off valve 70.
- A3 shows the actual amount of lubrication of the engaging element 80 in the open state of the on-off valve 70 when the on-off valve 70 is provided on the oil catch plate 60.
- B1 indicates a target lubrication amount of the planetary gear 1 (the bearing 32 between the pinion gear 30 and the pinion shaft 40) (optimal lubrication amount that is neither over-lubricated nor under-lubricated in the planetary gear 1), and B2 represents the oil catch plate 60.
- the actual lubrication amount of the planetary gear 1 when the on-off valve 70 is not provided is shown.
- B3 indicates the actual lubrication amount of the planetary gear 1 when the on-off valve 70 is open when the on-off valve 70 is provided on the oil catch plate 60. Show.
- the target lubrication amount A1 required by the engagement element 80 increases, but the target lubrication amount B1 required by the planetary gear 1 is The target lubrication amount A1 required by the engagement element 80 does not increase as much.
- the centrifugal force increases as the rotational speed of the oil catch plate 60 increases, the amount of lubrication released (scattered) from the guide hole 20a of the carrier 20 increases.
- the on / off valve 70 is not provided in the oil catch plate 60
- the lubrication amount for the planetary gear 1 and the lubrication amount for the engagement element 80 increase at a constant rate, so that the rotation speed of the oil catch plate 60 is increased.
- the lubrication amount A2 in the engagement element 80 becomes significantly less than the target lubrication amount A1.
- the lubrication amount B2 in the planetary gear 1 is significantly larger than the target lubrication amount B1.
- the on / off valve 70 is opened when the rotation speed R of the oil catch plate 60 reaches a predetermined rotation speed R1.
- a part of the lubricating oil taken into the lubricating groove 64 of the oil catch plate 60 through the oil passage L1 is guided to the engagement element 80 through the on-off valve 70 (oil passage L3).
- the lubrication amount which passes the on-off valve 70 increases, so that the rotation speed of the carrier 20 rises. Therefore, the lubrication amount A3 in the engagement element 80 approaches the target lubrication amount A1, and the lubrication amount B3 in the planetary gear 1 approaches the target lubrication amount B1.
- the lubricating oil supplied from the input shaft 2 side is in the middle of the oil passage (oil passage L1) for guiding the lubricating oil to the pinion gear 30 side of the planetary gear 1 (the lubricating groove of the oil catch plate 60). Since the opening / closing valve 70 that opens the valve at a predetermined number of revolutions or more is provided on the outer peripheral side of 64, the ratio (the difference) of the lubrication amount of each part (planetary gear 1, engagement element 80) changes due to the change in the number of revolutions. Even if this occurs, the distribution (balance) of the lubrication amount with respect to each part can be adjusted according to the change.
- the on-off valve 70 is provided on the oil catch plate 60 that rotates as the input shaft 2 rotates, and is configured to be opened by the centrifugal force that accompanies the rotation of the input shaft 2. Therefore, the on-off valve 70 can be automatically opened according to the rotational speed of the input shaft 2, and the distribution of the lubrication amount between the planetary gear 1 and the engaging element 80 can be adjusted appropriately.
- the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the claims and the technical idea described in the specification and drawings. Can be modified.
- the lubricating oil guide member (oil catch plate) according to the present invention is integrated with the carrier. It is also possible to configure.
- the oil catch plate 60 shown in the said embodiment is an example of the lubricating oil guide member concerning this invention. Therefore, the specific shape or the like of the lubricating oil guide member according to the present invention is not limited to the shape or the like provided in the oil catch plate 60.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
Abstract
Description
Claims (4)
- 回転軸を中心に所定の関係にて配置された複数の回転要素を有するプラネタリギヤと、
該プラネタリギヤの外周側に配置された係合要素と、
前記プラネタリギヤに取り付けた潤滑油を案内するための潤滑油案内部材と、を備え、
前記潤滑油案内部材は、前記回転軸側から供給される潤滑油を前記プラネタリギヤの内部に誘導する第1の油路と、
前記回転軸側から供給される潤滑油を前記係合要素に誘導する第2の油路と、
前記第1の油路を流通する潤滑油の一部を前記係合要素に誘導する第3の油路と、
前記第3の油路を開閉するための開閉手段と、を備え、
前記開閉手段は、前記潤滑油案内部材の回転数が所定の回転数以上になった場合に該第3の油路を開放する
ことを特徴とする駆動力伝達装置の潤滑構造。 - 前記開閉手段は、付勢手段の付勢力で弁体が弁座部に着座していることで前記第3の油路を閉じている開閉弁であり、前記潤滑油案内部材の回転により前記弁体にかかる遠心力で該弁体が前記付勢手段の付勢力に抗して前記弁座部から離間するように構成した
ことを特徴とする請求項1に記載の駆動力伝達装置の潤滑構造。 - 前記潤滑油案内部材は、円形環状の平板状に形成された部材であり、
前記第1の油路は、前記潤滑油案内部材の内径側に形成された外径側へ窪む溝部を含み、前記第3の油路は、前記溝部から前記潤滑油案内部材の外周縁に連通する連通路である
ことを特徴とする請求項1又は2に記載の駆動力伝達装置の潤滑構造。 - 前記第1の油路は、前記溝部から前記潤滑油案内部材を貫通して前記プラネタリギヤ側へ延びる筒状の通路を含み、
前記プラネタリギヤは、前記回転軸上に設置したサンギヤと、前記サンギヤの外径側で複数のピニオンギヤ及びピニオンシャフトを支持してなるキャリアと、前記キャリアの外径側で前記ピニオンギヤに噛合するリングギヤと、を備え、
前記筒状の通路は、前記回転軸側から供給される潤滑油を前記ピニオンシャフトを介して前記ピニオンギヤの回転摺接部分に誘導する
ことを特徴とする請求項3に記載の駆動力伝達装置の潤滑構造。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201380046822.7A CN104620024B (zh) | 2012-10-03 | 2013-09-25 | 驱动力传递装置的润滑结构 |
JP2014539681A JP5957086B2 (ja) | 2012-10-03 | 2013-09-25 | 駆動力伝達装置の潤滑構造 |
US14/432,876 US9447863B2 (en) | 2012-10-03 | 2013-09-25 | Lubrication structure for driving force transmission device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012221024 | 2012-10-03 | ||
JP2012-221024 | 2012-10-03 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014054490A1 true WO2014054490A1 (ja) | 2014-04-10 |
Family
ID=50434818
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2013/075957 WO2014054490A1 (ja) | 2012-10-03 | 2013-09-25 | 駆動力伝達装置の潤滑構造 |
Country Status (4)
Country | Link |
---|---|
US (1) | US9447863B2 (ja) |
JP (1) | JP5957086B2 (ja) |
CN (1) | CN104620024B (ja) |
WO (1) | WO2014054490A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016206745A1 (de) * | 2016-04-21 | 2017-10-26 | Zf Friedrichshafen Ag | Planetengetriebe |
CN108087533A (zh) * | 2017-11-29 | 2018-05-29 | 中国航发沈阳黎明航空发动机有限责任公司 | 一种燃气轮机中央锥传动装置导流片结构 |
WO2018147161A1 (ja) * | 2017-02-08 | 2018-08-16 | 武蔵精密工業株式会社 | 伝動装置 |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107614939B (zh) * | 2015-11-12 | 2020-02-07 | 株式会社小松制作所 | 润滑装置 |
JP6412060B2 (ja) * | 2016-05-30 | 2018-10-24 | 株式会社Subaru | 車両の駆動力伝達装置 |
US10975955B2 (en) * | 2018-08-24 | 2021-04-13 | Dana Automotive Systems Group, Llc | Planetary gear system |
DE102018217384A1 (de) * | 2018-10-11 | 2020-04-16 | Zf Friedrichshafen Ag | Innenlamellenträger für eine nasslaufende Reibkupplung |
CN111750045B (zh) * | 2019-03-29 | 2022-03-15 | 比亚迪股份有限公司 | 行星减速装置、驱动桥总成及车辆 |
JP2020183797A (ja) * | 2019-05-09 | 2020-11-12 | 本田技研工業株式会社 | 動力伝達装置 |
FR3098562B1 (fr) * | 2019-07-08 | 2021-06-11 | Safran Trans Systems | Couvercle de canalisation d’huile et reducteur mecanique de turbomachine d’aeronef comportant un tel couvercle |
EP3786487B1 (en) * | 2019-09-02 | 2022-11-09 | Mazda Motor Corporation | Control device for automatic transmission, automatic transmission, vehicle, and method of controlling automatic transmission |
KR102307705B1 (ko) * | 2019-12-10 | 2021-10-01 | 현대트랜시스 주식회사 | 자동변속기의 윤활장치 |
EP4086475A4 (en) * | 2019-12-30 | 2023-09-13 | Jatco Ltd | POWER TRANSMISSION DEVICE |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH031353U (ja) * | 1989-05-30 | 1991-01-09 | ||
JPH04337153A (ja) * | 1991-05-09 | 1992-11-25 | Jatco Corp | 自動変速機の摩擦締結装置の潤滑装置 |
JP2000337484A (ja) * | 1999-05-25 | 2000-12-05 | Daihatsu Motor Co Ltd | 遊星歯車装置の潤滑構造 |
JP2004028291A (ja) * | 2002-06-28 | 2004-01-29 | Aisin Aw Co Ltd | 自動変速機 |
JP2005061450A (ja) * | 2003-08-18 | 2005-03-10 | Aisin Aw Co Ltd | 自動変速機の潤滑油供給構造及び自動変速機用の環状レシーバ |
JP2010174917A (ja) * | 2009-01-27 | 2010-08-12 | Toyota Motor Corp | 自動変速機 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63275854A (ja) * | 1987-05-02 | 1988-11-14 | Aisin Warner Ltd | 自動変速機 |
DE19800490C2 (de) * | 1997-01-31 | 2000-02-24 | Audi Ag | Vorrichtung zur Kühlung zweier auf einer Getriebewelle angeordneter Lamellenkupplungen |
JP2000145933A (ja) | 1998-11-13 | 2000-05-26 | Aichi Mach Ind Co Ltd | 自動変速機におけるピニオン軸への給油構造 |
JP4340933B2 (ja) | 1999-02-18 | 2009-10-07 | 株式会社ジェイテクト | 遊星変速機構 |
JP3996154B2 (ja) | 2004-09-24 | 2007-10-24 | ジヤトコ株式会社 | 遊星歯車機構における潤滑構造 |
JP2007100926A (ja) | 2005-10-07 | 2007-04-19 | Toyota Motor Corp | 自動変速機 |
DE102007023953B4 (de) * | 2007-05-23 | 2016-02-04 | Zf Friedrichshafen Ag | Planetengetriebe mit einer Lamellenkupplung oder einer Lamellenbremse |
JP5167808B2 (ja) | 2007-07-06 | 2013-03-21 | アイシン・エィ・ダブリュ株式会社 | 自動変速機の潤滑油供給装置 |
WO2009008192A1 (ja) * | 2007-07-06 | 2009-01-15 | Aisin Aw Co., Ltd. | 自動変速機の潤滑油供給装置 |
-
2013
- 2013-09-25 US US14/432,876 patent/US9447863B2/en active Active
- 2013-09-25 WO PCT/JP2013/075957 patent/WO2014054490A1/ja active Application Filing
- 2013-09-25 CN CN201380046822.7A patent/CN104620024B/zh active Active
- 2013-09-25 JP JP2014539681A patent/JP5957086B2/ja not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH031353U (ja) * | 1989-05-30 | 1991-01-09 | ||
JPH04337153A (ja) * | 1991-05-09 | 1992-11-25 | Jatco Corp | 自動変速機の摩擦締結装置の潤滑装置 |
JP2000337484A (ja) * | 1999-05-25 | 2000-12-05 | Daihatsu Motor Co Ltd | 遊星歯車装置の潤滑構造 |
JP2004028291A (ja) * | 2002-06-28 | 2004-01-29 | Aisin Aw Co Ltd | 自動変速機 |
JP2005061450A (ja) * | 2003-08-18 | 2005-03-10 | Aisin Aw Co Ltd | 自動変速機の潤滑油供給構造及び自動変速機用の環状レシーバ |
JP2010174917A (ja) * | 2009-01-27 | 2010-08-12 | Toyota Motor Corp | 自動変速機 |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016206745A1 (de) * | 2016-04-21 | 2017-10-26 | Zf Friedrichshafen Ag | Planetengetriebe |
US10240670B2 (en) | 2016-04-21 | 2019-03-26 | Zf Friedrichshafen Ag | Planetary gearing |
WO2018147161A1 (ja) * | 2017-02-08 | 2018-08-16 | 武蔵精密工業株式会社 | 伝動装置 |
US11047467B2 (en) | 2017-02-08 | 2021-06-29 | Musashi Seimitsu Industry Co., Ltd. | Transmission device |
CN108087533A (zh) * | 2017-11-29 | 2018-05-29 | 中国航发沈阳黎明航空发动机有限责任公司 | 一种燃气轮机中央锥传动装置导流片结构 |
Also Published As
Publication number | Publication date |
---|---|
CN104620024B (zh) | 2017-03-08 |
JPWO2014054490A1 (ja) | 2016-08-25 |
JP5957086B2 (ja) | 2016-07-27 |
US9447863B2 (en) | 2016-09-20 |
CN104620024A (zh) | 2015-05-13 |
US20150292613A1 (en) | 2015-10-15 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5957086B2 (ja) | 駆動力伝達装置の潤滑構造 | |
US8523725B2 (en) | Lubricating structure of speed change mechanism | |
US8821332B2 (en) | Power transmission device | |
US8911318B2 (en) | Pinion lubrication structure of planetary gear mechanism | |
US8167756B2 (en) | Lubricating oil supply device for automatic transmission | |
US20070082778A1 (en) | Automatic transmission | |
US7025704B2 (en) | Planetary gear for automatic transmission | |
US20080268997A1 (en) | Lubrication path in a planetary gear unit for a transmission | |
US9885404B2 (en) | Power transfer device | |
JP2009036369A (ja) | 自動変速機の潤滑油供給装置 | |
JP5968199B2 (ja) | 駆動力伝達装置の潤滑構造 | |
US10520030B2 (en) | Structure with bearing and bearing | |
CN107407350B (zh) | 变速装置 | |
US20160281836A1 (en) | Automatic transmission | |
JP6333613B2 (ja) | オイルレシーバ | |
JP2009222178A (ja) | 遊星歯車装置の潤滑構造 | |
JP2008039164A (ja) | 遊星歯車機構ならびに車両用変速機 | |
JP2009168070A (ja) | デファレンシャル装置 | |
JP5082634B2 (ja) | 自動変速機の潤滑油供給装置 | |
JP4417214B2 (ja) | 自動変速機の軸受潤滑構造 | |
JP4970395B2 (ja) | 車両用自動変速機の潤滑構造 | |
JP2015200396A (ja) | 車両用動力伝達機構 | |
JP5962581B2 (ja) | 変速機の潤滑装置 | |
JP2013204754A (ja) | 動力伝達装置 | |
KR20090089709A (ko) | 유성기어 세트 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 13844488 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2014539681 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14432876 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 13844488 Country of ref document: EP Kind code of ref document: A1 |