WO2013046550A1 - 自動変速機 - Google Patents
自動変速機 Download PDFInfo
- Publication number
- WO2013046550A1 WO2013046550A1 PCT/JP2012/005635 JP2012005635W WO2013046550A1 WO 2013046550 A1 WO2013046550 A1 WO 2013046550A1 JP 2012005635 W JP2012005635 W JP 2012005635W WO 2013046550 A1 WO2013046550 A1 WO 2013046550A1
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- WO
- WIPO (PCT)
- Prior art keywords
- axial direction
- balance chamber
- automatic transmission
- centrifugal balance
- friction plate
- Prior art date
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Classifications
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
-
- 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
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0661—Hydraulically actuated multiple lamellae clutches
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0224—Details of conduits, connectors or the adaptors therefor specially adapted for clutch control
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/104—Clutch
- F16D2500/10443—Clutch type
- F16D2500/1045—Friction clutch
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/108—Gear
- F16D2500/1081—Actuation type
- F16D2500/1085—Automatic 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/50—Problem to be solved by the control system
- F16D2500/51—Relating safety
- F16D2500/5104—Preventing failures
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
Definitions
- the present invention relates to an automatic transmission in which a centrifugal balance chamber is arranged to overlap with a friction plate in the axial direction.
- Patent Document 1 discloses a centrifugal cancel plate that forms a centrifugal cancel chamber (centrifugal balance chamber) with a clutch piston.
- a drum clutch of an automatic transmission in which a long hole (through hole) for discharging hydraulic oil to the outside is formed in (seal plate) is disclosed.
- the friction plate and the centrifugal cancel chamber may be arranged at a position where they do not overlap in the axial direction so that the hydraulic oil discharged from the centrifugal cancel chamber is not applied to the friction plate.
- the present invention has been made in view of the above points, and an object of the present invention is to make an axial transmission compact in an automatic transmission in which a centrifugal balance chamber is arranged to overlap with a friction plate in the axial direction. It is providing the technique which suppresses deterioration of a fuel consumption, maintaining fuel consumption.
- the hydraulic oil in the centrifugal balance chamber is discharged to a position where it does not contact the friction plate without changing the positional relationship between the centrifugal balance chamber and the friction plate. ing.
- the first invention is a friction plate for fastening a drum and a hub to transmit power from a drive source input via an input shaft, and a radial direction from the friction plate.
- the fastening hydraulic chamber and the centrifugal balance chamber located inside, the fastening hydraulic chamber and the centrifugal balance chamber are partitioned in the axial direction, and the friction plate is fastened or tightened based on the pressure difference between the hydraulic oils in these chambers.
- An automatic transmission including a friction fastening element having a piston to be released and having the centrifugal balance chamber disposed in an axially overlapping manner with the friction plate.
- the hydraulic balance chamber is further provided with a discharge means for discharging the hydraulic oil in the centrifugal balance chamber to a position where it does not overlap the friction plate in the axial direction.
- the hydraulic oil in the centrifugal balance chamber does not overlap with the friction plate in the axial direction (of the input shaft) by the discharging means. In other words, it is discharged to a position that does not touch the friction plate. Therefore, deterioration of fuel consumption can be suppressed while maintaining compactness in the axial direction of the automatic transmission by arranging the centrifugal balance chamber and the friction plate so as to overlap in the axial direction.
- the second invention is characterized in that, in the first invention, the discharge means is disposed radially inward of the centrifugal balance chamber.
- the discharging means is disposed further radially inward than the centrifugal balance chamber located radially inward of the friction plate, the fastening is aligned in the axial direction with the centrifugal balance chamber.
- the hydraulic oil in the centrifugal balance chamber can be discharged to a position that does not overlap the friction plate in the axial direction without affecting the arrangement structure of the hydraulic chamber, the friction plate, the piston, and the like.
- the apparatus further includes a cylindrical member that interpolates and supports the input shaft, and the discharge means includes an oil passage that is formed in the cylindrical member and extends in the axial direction.
- the end on the side opposite to the drive source in the axial direction of the oil passage communicates with the centrifugal balance chamber, while the end on the drive source side in the axial direction of the oil passage communicates with the friction plate.
- the exhaust oil passage is provided so as to extend in the radial direction at a position where it does not overlap in the axial direction.
- the discharging means disposed on the radially inner side of the centrifugal balance chamber using the existing components of the automatic transmission without adding new members or the like. can do.
- the drain oil passage further includes a shaft of a frictional engagement element closest to the front cover that closes the end portion on the drive source side in the axial direction of the transmission case. It is formed on the drive source side in the direction.
- the hydraulic oil in the centrifugal balance chamber passes through the discharge oil passage, and the frictional engagement element drum closest to the front cover that closes the end on the drive source side in the axial direction of the transmission case. Since it is discharged to the outside, it is possible to suppress the occurrence of rotational resistance not only between the friction plates but also between members provided on the inside of the drum that cause differential rotation.
- the cylindrical plate and the seal plate disposed to face the piston in the axial direction so that the centrifugal balance chamber is formed between the piston and the piston.
- a sleeve that is connected to the input shaft and supports the inner peripheral portion of the seal plate at an outer peripheral portion thereof, and further includes an end on the counter drive source side in the axial direction of the cylindrical member The portion is formed with a substantially annular space that is surrounded by the end of the cylindrical member, the input shaft, and the sleeve, and communicates with the oil passage.
- the sleeve and the centrifugal balance are formed in the sleeve.
- a through hole extending in the radial direction is formed to communicate with the chamber, and the hydraulic oil flowing from the centrifugal balance chamber via the space to the oil passage is prevented from leaking to the friction plate side.
- Above And blanking and the input shaft is characterized in that it is welded.
- the hydraulic oil that flows through the through hole formed in the sleeve from the centrifugal balance chamber and flows into the oil passage via the space surrounded by the end of the cylindrical member, the input shaft, and the sleeve By suppressing leakage to the friction plate side, it is possible to reliably suppress deterioration of fuel consumption.
- a sixth invention is characterized in that, in any one of the first to fifth inventions, the input shaft is mounted on a vehicle in a horizontal arrangement with the input shaft directed in the vehicle width direction. .
- the centrifugal balance chamber and the friction plate are arranged in such a manner that the centrifugal balance chamber is disposed so as to overlap the friction plate in the axial direction. Without changing the positional relationship, the hydraulic oil in the centrifugal balance chamber is discharged to a position that does not overlap the friction plate in the axial direction by the discharging means, so that the automatic transmission is kept compact in the axial direction, Deterioration of fuel consumption can be suppressed.
- FIG. 1 is a longitudinal sectional view showing a portion above an axis of an input shaft of a clutch pack of an automatic transmission according to an embodiment of the present invention.
- FIG. 2 is a rear view of the front cover as viewed from the anti-torque converter side.
- FIG. 3 is a longitudinal sectional view of the front cover.
- FIG. 1 is a view showing a portion above the axis of the input shaft of the clutch pack of the automatic transmission according to the present embodiment.
- the automatic transmission 1 is mounted on a horizontally mounted engine vehicle such as a front engine front drive vehicle, and the power from a torque converter (drive source) 11 attached to an engine output shaft (not shown) receives the input shaft 13.
- the first and second clutches 5 and 7 input through the transmission, a transmission mechanism (not shown) to which power is input from one or both of the clutches 5 and 7, and the first and second clutches 5 and 5.
- 7 and a transmission case 31 that houses the transmission mechanism.
- the assembly of the components of the first clutch 5 and the second clutch 7 and the sleeve 23 is referred to as “clutch pack 3”.
- the torque converter side (drive source side) in the axial direction is referred to as “front side”
- the anti-torque converter side (counter drive source side) in the axial direction is referred to as “rear side”.
- the first clutch (friction engagement element) 5 is a multi-plate clutch, and includes a first drum 25 and a first hub 35, and a torque converter 11 that is input via the input shaft 13.
- the first centrifugal balance chamber 75 is formed between the first piston 45 and the first fastening hydraulic chamber 65 and the first centrifugal balance chamber 75 to which hydraulic oil for pressing the first piston 45 is supplied.
- the first seal plate 55 is disposed opposite to the first piston 45 in the axial direction.
- the second clutch (friction engagement element) 7 is also a multi-plate clutch, and the power from the torque converter 11 input via the second drum 27 and the second hub 37 and the input shaft 13 is changed to a speed change mechanism.
- the second centrifugal balance chamber 77 is formed between the second piston 47 and the second fastening hydraulic chamber 67 and the second centrifugal balance chamber 77 to which hydraulic oil for pressing the pressure 47 is supplied. It has the piston 47 and the 2nd seal plate 57 arrange
- the plurality of first friction plates 15 are arranged in parallel with the plurality of second friction plates 17, in other words, so as to overlap the plurality of second friction plates 17 in the axial direction of the input shaft 13 (the radial direction of the input shaft 13).
- the second friction plates 17 are arranged on the radially outer side of the second friction plates 17 so as to overlap the second friction plates 17.
- the first drum 25 supports a plurality of first friction plates 15 movably in the axial direction on the outer peripheral side of the first friction plates 15 so as to cover the radially outer side and the front side of the second clutch 7. It is arrange
- the first hub 35 supports the plurality of first friction plates 15 so as to be movable in the axial direction on the inner peripheral side of the first friction plates 15 and is arranged so as to cover the rear side of the second clutch 7.
- the inner peripheral end 35a is connected to the clutch output member 33.
- the first engagement hydraulic chamber 65 and the first centrifugal balance chamber 75 are adjacent to the front side of the second clutch 7, a first seal plate 55 whose inner peripheral end 55 a is supported by the sleeve 23, It is located between the first drum 25 and is partitioned in the axial direction by a first piston 45 that fastens or releases the plurality of second friction plates 17 based on the pressure difference between the hydraulic oils in these chambers. ing.
- the space defined by the first drum 25 and the first piston 45 constitutes the first fastening hydraulic chamber 65 and is defined by the first piston 45 and the first seal plate 55.
- the first space constitutes the first centrifugal balance chamber 75.
- first fastening hydraulic pressure is applied to the inner peripheral end 45 a of the first piston 45 that contacts the sleeve 23 and the outer peripheral end 55 b of the first seal plate 55 that contacts the inner peripheral surface of the first piston 45.
- a lip seal for oil-tightening the chamber 65 and the first centrifugal balance chamber 75 is attached.
- Reference numeral 85 in the first centrifugal balance chamber 75 is a return spring that is mounted between the first piston 45 and the first seal plate 55 and biases the first piston 45 in the release direction (front side). Show.
- the first clutch 5 is disposed so as to cover the front side, the rear side, and the radially outer side of the second clutch 7, so that the first drum 25 can change the speed change according to the present invention.
- This corresponds to the drum of the frictional engagement element closest to the front cover 21 that closes the front end of the machine case 31.
- the second drum 27 supports a plurality of second friction plates 17 so as to be movable in the axial direction on the outer peripheral side of the second friction plates 17, and the first hub 35 and the second friction plates in the radial direction. 17 and an end portion 27 a on the inner peripheral side thereof is fixed to the sleeve 23.
- the second hub 37 supports a plurality of second friction plates 17 so as to be movable in the axial direction on the inner peripheral side of the second friction plates 17, and is disposed on the front side of the first hub 35.
- the end 37a on the inner peripheral side is connected to the output member 43 of the clutch.
- the second fastening hydraulic chamber 67 and the second centrifugal balance chamber 77 are radially inward of the second friction plate 17 and have a second seal plate 57 whose inner peripheral end 57a is supported by the sleeve 23.
- the second piston 47 is positioned between the second drum 27 and is partitioned in the axial direction by a second piston 47 that fastens or releases the plurality of second friction plates 17 based on the pressure difference between the hydraulic oils in the chambers. It has been.
- the space defined by the second drum 27 and the second piston 47 constitutes the second fastening hydraulic chamber 67 and is defined by the second piston 47 and the second seal plate 57.
- the second centrifugal balance chamber 77 constitutes a second centrifugal balance chamber 77, and the second centrifugal balance chamber 77 overlaps with the second friction plate 17 in the axial direction (when viewed from the radial direction of the input shaft 13, a plurality of second It is provided so as to overlap with the friction plate 17.
- the second fastening hydraulic pressure is applied to the inner peripheral end portion 47 a of the second piston 47 in contact with the sleeve 23 and the outer peripheral end portion 57 b of the second seal plate 57 in contact with the inner peripheral surface of the second piston 47.
- a lip seal for oil-tightening the chamber 67 and the second centrifugal balance chamber 77 is attached.
- Reference numeral 87 in the second centrifugal balance chamber 77 is a return spring that is mounted between the second piston 47 and the second seal plate 57 and biases the second piston 47 in the releasing direction (front side). Show.
- the arrangement structure of the clutch pack 3 as described above that is, the plurality of second friction plates 17 are arranged inside the plurality of first friction plates 15 in the radial direction, and the inside of the plurality of second friction plates 17 in the radial direction.
- the automatic transmission 1 of the present embodiment is made compact in the axial direction (vehicle width direction).
- the end portions 25a, 27a on the inner peripheral side of the first and second drums 25, 27 are fixed, and the first and second seal plates 55, 57 are supported by the end portions 55a, 57a on the inner peripheral side.
- the sleeve 23 is formed on a boss portion (tubular member) 41 that is formed integrally with the front cover 21 and extends from the central portion of the rear side surface of the front cover 21 toward the rear side so as to insert and support the input shaft 13. It is externally fitted so that it can slide and rotate.
- the sleeve 23 is formed with an annular step 23a protruding radially inward at a portion extending further to the rear side than the tip (rear end surface 41a) of the boss portion 41.
- the sleeve 23 is externally fitted to the boss portion 41 and connected to the input shaft 13, so that the end surface 41 a of the boss portion 41 is input to the rear end portion of the boss portion 41.
- a substantially annular space 19 surrounded by the shaft 13 and the sleeve 23 is formed.
- the sleeve 23 is externally fitted to the boss portion 41, and the step portion 23 a of the sleeve 23 is connected to the flange portion 13 a of the input shaft 13.
- a first oil passage 29 for supplying hydraulic oil to the second centrifugal balance chamber 77 extending in the axial direction is formed in the boss portion 41.
- an oil passage for supplying hydraulic oil to the first fastening hydraulic chamber 65, the first centrifugal balance chamber 75, and the second fastening hydraulic chamber 67 is also provided in the boss portion 41.
- the front end of the first oil passage 29 is formed in the front cover 21 so as to extend obliquely downward from the center of the front cover 21 and is driven by the engine via the torque converter 11. It communicates with a supply oil passage 49 to which hydraulic oil from (not shown) is supplied.
- the rear end portion of the first oil passage 29 communicates with the second centrifugal balance chamber 77 through an oil passage (not shown) formed in the sleeve 23.
- the automatic transmission 1 does not overlap the hydraulic oil in the second centrifugal balance chamber 77 in the axial direction with the second friction plate 17 (when viewed from the radial direction of the input shaft 13), 2 is further provided with a discharge means disposed radially inward of the second centrifugal balance chamber 77 for discharging to a position that does not overlap the two friction plates 17.
- the discharging means has a second oil passage 9 formed in the boss portion 41 and extending in the axial direction.
- the second oil passage 9 has a rear end portion communicating with the second centrifugal balance chamber 77 and a front end portion not overlapping the second friction plate 17 in the axial direction. And communicates with a drain oil passage 39 provided to extend in the radial direction.
- the rear end of the second oil passage 9 communicates with the space 19, and the space 19 and the second centrifugal balance chamber 77 are formed in the portion of the sleeve 23 where the step 23 a is formed.
- a through-hole 23b extending in the radial direction is formed.
- the rear end of the second oil passage 9 communicates with the second centrifugal balance chamber 77 via the space 19 and the through hole 23b.
- the front end of the second oil passage 9 communicates with a discharge oil passage 39 formed in the front cover 21 so as to extend obliquely upward from the center portion of the front cover 21.
- excess hydraulic oil in the second centrifugal balance chamber 77 passes through the through hole 23b formed in the sleeve 23 and then passes through the space 19 to the second oil passage. It flows into 9.
- the spline formed on the inner peripheral surface of the tip of the sleeve 23 and the spline formed on the corresponding outer peripheral surface of the input shaft 13 are engaged with each other to thereby input the sleeve 23 and the input.
- the automatic transmission 1 of this embodiment is connected to the shaft 13 by welding the step portion 23a of the sleeve 23 and the flange portion 13a of the input shaft 13 as described above. Therefore, the hydraulic oil flowing from the second centrifugal balance chamber 77 through the space 19 to the second oil passage 9 can be prevented from leaking to the second friction plate 17 side. .
- the hydraulic oil that has flowed in the second oil passage 9 from the rear side to the front side reaches the front cover 21, it flows in the discharge oil passage 39 formed in the front cover 21 and flows into the first drum. 25 is discharged to the outside.
- the hydraulic oil is discharged from the discharge oil passage 39 provided further on the front side than the first drum 25 in a position where the second friction plate 17 does not overlap in the axial direction.
- the two friction plates 17, for example, between the first hub 35 and the first seal plate 55, and so on it is possible to suppress the occurrence of rotational resistance between the members that are provided inside the first drum 25 and cause differential rotation. Can do.
- the hydraulic oil is pushed obliquely upward through the discharge oil passage 39, but the supply oil passage 49, the first oil passage 29, the second centrifugal balance chamber 77, the through hole 23b, the space 19, the second oil passage 9,
- the hydraulic oil can be pushed obliquely upward only by the supply force of the oil pump without using a separate pump or the like for sucking out the hydraulic oil. .
- the hydraulic oil in the second centrifugal balance chamber 77 is discharged from the second friction plate 17 by the discharge means.
- the second friction plate 17 is discharged to a position where it does not overlap in the axial direction (of the input shaft 13).
- the discharging means is provided further radially inward than the second centrifugal balance chamber 77 located radially inward of the second friction plate 17, it is aligned with the second centrifugal balance chamber 77 in the axial direction. Without affecting the arrangement structure of the second fastening hydraulic chamber 67, the second friction plate 17, the second piston 47, etc., the hydraulic oil in the second centrifugal balance chamber 77 exceeds the second friction plate 17 in the axial direction. It can be discharged to a position where it does not wrap.
- the hydraulic oil in the second centrifugal balance chamber 77 is discharged to the outside of the first drum 25 closest to the front cover 21 that closes the front end of the transmission case 31 via the discharge oil passage 39. Therefore, it is possible to suppress the occurrence of rotational resistance not only between the second friction plates 17 but also between members that are provided on the inner side of the first drum 25 and cause differential rotation.
- the hydraulic oil flowing from the second centrifugal balance chamber 77 to the second oil passage 9 via the space 19 is 2 Leakage toward the friction plate 17 can be suppressed, and deterioration of fuel consumption can be reliably suppressed.
- the hydraulic oil is discharged from the discharge oil passage 39 provided further on the front side than the first drum 25.
- the hydraulic oil is not overlapped with the second friction plate 17 in the axial direction. If discharged, the discharged oil passage 39 may be provided on the rear side of the first drum 25.
- the step portion 23a of the sleeve 23 and the flange portion 13a of the input shaft 13 are welded.
- the present invention is not limited to this.
- spline fitting formed on the inner peripheral surface of the tip of the sleeve 23.
- a spline formed on the corresponding outer peripheral surface of the input shaft 13 may be used.
- the drive source is a torque converter.
- the hydraulic oil is supplied from the first oil passage 29 communicating with the supply oil passage 49 to the second centrifugal balance chamber 77 and discharged from the second oil passage 9 communicating with the discharge oil passage 39.
- the present invention is not limited thereto, and the working oil is supplied from the second oil passage 9 to the second centrifugal balance chamber 77 using the discharge oil passage 39 as an oil passage for supplying the working oil.
- the hydraulic oil may be discharged from the first oil passage 29 using the passage 49 as an oil passage for discharging the hydraulic oil.
- the present invention is useful for an automatic transmission or the like in which the centrifugal balance chamber is disposed so as to overlap the friction plate in the axial direction.
- Second clutch (friction engagement element) Second clutch (friction engagement element) 9 Second oil passage (oil passage) (discharge means) 11 Torque converter (drive source) 13 Input shaft 17 Second friction plate (friction plate) 19 Space 21 Front cover 23 Sleeve 23b Through hole 25 First drum (drum) 27 Second drum (drum) 37 Second Hub (Hub) 39 Oil discharge passage 41 Boss part (tubular member) 47 Second piston (piston) 57 Second seal plate (seal plate) 67 Second fastening hydraulic chamber (fastening hydraulic chamber) 77 Second centrifugal balance chamber (centrifugal balance chamber)
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
本実施形態によれば、第2遠心バランス室77と第2摩擦板17との位置関係を変えることなく、第2遠心バランス室77内の作動油が、排出手段によって、第2摩擦板17と(入力軸13の)軸方向にオーバーラップしない位置に、換言すると、第2摩擦板17にかからない位置に排出される。これにより、自動変速機1の軸方向(車幅方向)におけるコンパクト化を維持しつつ、燃費の悪化を抑制することができる。
本発明は、実施形態に限定されず、その精神又は主要な特徴から逸脱することなく他の色々な形で実施することができる。
5 第1クラッチ(摩擦締結要素)
7 第2クラッチ(摩擦締結要素)
9 第2油路(油路)(排出手段)
11 トルクコンバータ(駆動源)
13 入力軸
17 第2摩擦板(摩擦板)
19 空間
21 フロントカバー
23 スリーブ
23b 貫通孔
25 第1ドラム(ドラム)
27 第2ドラム(ドラム)
37 第2ハブ(ハブ)
39 排出油路
41 ボス部(筒状部材)
47 第2ピストン(ピストン)
57 第2シールプレート(シールプレート)
67 第2締結油圧室(締結油圧室)
77 第2遠心バランス室(遠心バランス室)
Claims (6)
- 入力軸を介して入力される駆動源からの動力を伝達するために、ドラムとハブとを締結するための摩擦板と、当該摩擦板よりも径方向内側に位置する締結油圧室及び遠心バランス室と、当該締結油圧室と当該遠心バランス室とを軸方向に仕切り、且つ、これらの室内の作動油の圧力差に基いて、当該摩擦板を締結又は解放させるピストンと、を有し、上記遠心バランス室が上記摩擦板と軸方向にオーバーラップして配設される摩擦締結要素、を備えた自動変速機であって、
上記遠心バランス室内の作動油を、上記摩擦板と軸方向にオーバーラップしない位置に排出するための排出手段をさらに備えていることを特徴とする自動変速機。 - 請求項1記載の自動変速機において、
上記排出手段は、上記遠心バランス室よりも径方向内側に配設されていることを特徴とする自動変速機。 - 請求項2記載の自動変速機において、
上記入力軸を内挿して支持する筒状部材をさらに備え、
上記排出手段は、上記筒状部材に形成された軸方向に延びる油路を有しており、
上記油路の軸方向における反駆動源側の端部は、上記遠心バランス室と連通している一方、上記油路の軸方向における駆動源側の端部は、上記摩擦板と軸方向にオーバーラップしない位置で径方向に延びるように設けられた排出油路と連通していることを特徴とする自動変速機。 - 請求項3記載の自動変速機において、
上記排出油路は、変速機ケースの軸方向における駆動源側の端部を閉塞するフロントカバーに最も近い摩擦締結要素のドラムよりもさらに、軸方向における駆動源側に形成されていることを特徴とする自動変速機。 - 請求項3記載の自動変速機において、
上記ピストンとの間に上記遠心バランス室が形成されるように、当該ピストンと軸方向に対向して配置されるシールプレートと、
上記筒状部材に外嵌合され且つ上記入力軸と連結されるとともに、その外周部で上記シールプレートの内周部を支持するスリーブと、をさらに備え、
上記筒状部材の軸方向における反駆動源側の端部には、当該筒状部材の端部と上記入力軸と上記スリーブとによって囲まれる、上記油路が連通する略環状の空間が形成されており、
上記スリーブには、上記空間と上記遠心バランス室とを連通する、径方向に延びる貫通孔が形成されており、
上記遠心バランス室から上記空間を経由して上記油路に流れる作動油が、上記摩擦板側へリークするのを抑えるために、上記スリーブと上記入力軸とが溶接されていることを特徴とする自動変速機。 - 請求項1~5のいずれか1つに記載の自動変速機において、
上記入力軸を車幅方向に向けた横置きの配置で、車両に搭載されていることを特徴とする自動変速機。
Priority Applications (3)
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DE112012004005.8T DE112012004005B4 (de) | 2011-09-26 | 2012-09-05 | Automatikgetriebe |
US14/345,220 US9353843B2 (en) | 2011-09-26 | 2012-09-05 | Automatic transmission |
CN201280044091.8A CN103827531B (zh) | 2011-09-26 | 2012-09-05 | 自动变速器 |
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JP2011209490A JP5790376B2 (ja) | 2011-09-26 | 2011-09-26 | 自動変速機 |
JP2011-209490 | 2011-09-26 |
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WO2013046550A1 true WO2013046550A1 (ja) | 2013-04-04 |
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PCT/JP2012/005635 WO2013046550A1 (ja) | 2011-09-26 | 2012-09-05 | 自動変速機 |
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US (1) | US9353843B2 (ja) |
JP (1) | JP5790376B2 (ja) |
CN (1) | CN103827531B (ja) |
DE (1) | DE112012004005B4 (ja) |
WO (1) | WO2013046550A1 (ja) |
Cited By (1)
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WO2015000482A1 (de) * | 2013-07-04 | 2015-01-08 | Schaeffler Technologies Gmbh & Co. Kg | Mehrfachkupplungseinrichtung für ein nutzfahrzeug sowie drehmomentübertragungseinrichtung oder kupplung |
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JP6555425B2 (ja) * | 2016-09-02 | 2019-08-07 | アイシン・エィ・ダブリュ株式会社 | 自動変速機 |
JP6920236B2 (ja) * | 2018-03-06 | 2021-08-18 | 本田技研工業株式会社 | 摩擦係合装置 |
DE102018122386A1 (de) * | 2018-09-13 | 2020-03-19 | Schaeffler Technologies AG & Co. KG | Doppelkupplungseinrichtung für einen Antriebsstrang eines Kraftfahrzeuges mit vollhydraulischer Betätigung |
JP7321426B2 (ja) * | 2019-11-18 | 2023-08-07 | マツダ株式会社 | 動力伝達装置 |
US11236786B2 (en) | 2020-01-09 | 2022-02-01 | Cnh Industrial America Llc | Multipart balanced piston clutch |
FR3111171B1 (fr) * | 2020-06-03 | 2022-10-14 | Valeo Embrayages | Double embrayage humide |
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2012
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- 2012-09-05 WO PCT/JP2012/005635 patent/WO2013046550A1/ja active Application Filing
- 2012-09-05 US US14/345,220 patent/US9353843B2/en not_active Expired - Fee Related
- 2012-09-05 DE DE112012004005.8T patent/DE112012004005B4/de active Active
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CN103827531A (zh) | 2014-05-28 |
DE112012004005B4 (de) | 2016-06-16 |
US20140345998A1 (en) | 2014-11-27 |
JP5790376B2 (ja) | 2015-10-07 |
CN103827531B (zh) | 2016-06-08 |
US9353843B2 (en) | 2016-05-31 |
JP2013072440A (ja) | 2013-04-22 |
DE112012004005T5 (de) | 2014-07-10 |
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