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
  • F16H—GEARING
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
  • F16H61/0009—Hydraulic control units for transmission control, e.g. assembly of valve plates or valve units
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
  • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
  • F16H63/30—Constructional features of the final output mechanisms
  • F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure
  • F16H63/3026—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure comprising friction 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
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H2061/0046—Details of fluid supply channels, e.g. within shafts, for supplying friction devices or transmission actuators with control fluid
• • 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
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
  • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
• • 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
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
  • F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
• • 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
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/20—Transmissions using gears with orbital motion
  • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
  • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
• • 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
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/20—Transmissions using gears with orbital motion
  • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
  • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
• • 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
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/20—Transmissions using gears with orbital motion
  • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
  • F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
• • 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
  • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
  • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
  • F16H3/62—Gearings having three or more central gears
  • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
  • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
• • 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
  • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
  • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
  • F16H3/62—Gearings having three or more central gears
  • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
  • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
• • 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

Definitions

• the present invention relates to a pressure oil supply device in an automatic transmission that supplies pressure oil to a hydraulic servo of a clutch that constitutes an automatic transmission.
• a clutch multiple structure is considered as one of the methods.
• the inner drum is usually assembled to the outer drum so as to be integrally rotatable by spline engagement or the like, and is attached to the inner drum.
• the hydraulic servo of the stored clutch is supplied with pressure oil through oil holes formed in the outer drum and the inner drum.
• oil holes formed in the drum for supplying pressure oil to the hydraulic servo are generally formed at equal intervals on the circumference.
• Patent Document 1 Japanese Patent Laid-Open No. 9-210088 (FIG. 2)
• first oil hole 65 and the second oil hole 65 The angle phase of hole 66 will cause a phase shift of up to 45 degrees.
• the hydraulic servo is The pressure oil supply path (supply length) increases, causing a delay in clutch engagement time.
• the second oil hole 66 should be aligned with the first oil hole 65 when the inner drum is assembled to the outer drum. In addition, it is necessary to place a mark on the drum for positioning. In addition, there is a problem that the assembly becomes troublesome and increases the cost.
• the present invention has been made in view of the above-described conventional problems.
• the first and the second drums when the second drum that does not increase the number of oil holes is arbitrarily assembled to the first drum. It is an object of the present invention to provide a pressure oil supply device in an automatic transmission that can minimize the phase shift of the second oil hole.
• the invention according to claim 1 includes a transmission mechanism that disengages and disengages a plurality of clutches and brakes to shift to a plurality of stages
• the transmission mechanism includes a first drum and A first hydraulic servo having a first piston that forms a first cylinder chamber together with the first drum, and a first hydraulic servo disposed on the outer periphery of the boss portion of the first drum and rotated integrally with the first drum.
• a second hydraulic servo having two drums and a second piston that forms a second cylinder chamber together with the second drum, and a pressure oil supply passage provided in the first drum and the second drum.
• the pressure oil supply passage is formed at a plurality of equiangular intervals on the circumference formed in the first drum.
• the first oil holes and the second oil holes communicate with each other.
• An annular oil passage force is used, and the number of the other oil holes is increased with respect to the number of the oil holes formed in one of the first and second oil holes. .
• the invention according to claim 2 is the invention according to claim 1, wherein the first and second oil holes are constituted by a plurality different from each other except a multiple.
• the invention according to claim 3 is the invention according to claim 2, in which one of the first and second oil holes. One of them is four and the other is six.
• the pressure oil supply passages provided in the first drum and the second drum have a plurality of first oil holes formed in the first drum at equal circumferential intervals on the circumference. And a plurality of second oil holes formed on the second drum at equiangular intervals on the circumference, and a pair of seal rings disposed between the first and second drums. And the second oil hole communicated with each other, and the number of the first and second oil holes is increased with respect to the number of oil holes formed in one of the two. Therefore, the phase shift of the first and second oil holes when the second drum is arbitrarily assembled to the first drum is compared with the case where the number of the first and second oil holes is the same. Therefore, the oil supply path (supply length) to the clutch due to a phase shift during assembly can be reduced. To become.
• the first and second oil holes are configured by a plurality different from each other excluding multiples, the second oil holes can be obtained without increasing the number of oil holes.
• the phase shift between the first and second oil holes when the drum is arbitrarily assembled to the first drum can be kept small.
• the phase shift of the first and second oil holes when the second drum is arbitrarily assembled to the first drum can be kept to a value as small as 15 degrees or less.
• FIG. 1 is a skeleton diagram showing an automatic transmission according to the present invention.
• FIG. 2 is a diagram showing engagement states of brakes and clutches at each gear stage of the automatic transmission in FIG.
• FIG. 3 is a cross-sectional view showing a pressure oil supply device for an automatic transmission according to an embodiment of the present invention.
• FIG. 4 is an enlarged view of a part of FIG.
• FIG. 5 is a cross-sectional view taken along line AA in FIG.
• FIG. 6 is an explanatory diagram showing the relationship between the first oil hole and the second oil hole shown in FIG.
• FIG. 7 is an explanatory view showing the relationship between the first oil hole and the second oil hole according to another embodiment of the present invention.
• FIG. 8 is an explanatory view showing a relationship between a first oil hole and a second oil hole according to still another embodiment of the present invention.
• FIG. 9 is an explanatory view showing a relationship between a first oil hole and a second oil hole according to still another embodiment of the present invention.
• FIG. 10 is an explanatory view showing a relationship between a first oil hole and a second oil hole as a comparative example.
• Oil hole 65 "'1st Oil hole, 66 ⁇ Second oil hole, 67 • ⁇ Roll oil passage, Sl, S2, S3 ⁇ 'Sun gear, Cl, C2, C3-' carrier, Rl, R2- "ring gear, C— 1 ⁇ 'First clutch, C— 2 ⁇ ' Second clutch, C— 3 ⁇ 'Third clutch, (3—4 ⁇ Fourth clutch, B— 1 ⁇ ⁇ First brake, B— 2 ⁇ Second brake.
• FIG. 1 shows an automatic transmission 10 suitable for use in, for example, a front engine rear drive type vehicle.
• the automatic speed changer 10 includes a torque converter 12 and a speed change mechanism 13 in a transmission case 11 attached to a vehicle body.
• the output from the engine is input to the input shaft 15 of the automatic transmission 10 via the pump inverter of the torque converter 12 and the turbine runner.
• the transmission mechanism 13 shifts the rotation input from the input shaft 15 and outputs it to the output shaft 16 connected to the drive wheels.
• the torque converter 12 is provided with a lockup clutch 17.
• the torque converter side in the axial direction of the automatic transmission is called “front”, and the output shaft side is called “rear”.
• the transmission mechanism 13 includes an input shaft 15 that is sequentially supported coaxially within the transmission case 11, a planetary gear 20 for reduction, a planetary gear set 21 that also includes a plurality of planetary gear forces, an output shaft 16, first through fourth Clutch C— 1 to C— 4 and first and second brakes B —1 and B—2
• a speed reduction planetary gear 20 that decelerates the rotation of the input shaft 15 and transmits it to the speed reduction rotating member is a sun gear S1 that is always fixed to the transmission case 11 and restricted in rotation, and a carrier C1 that is directly connected to the input shaft 15
• Planetary gear set 21 is, for example, configured as a rabbi-type gear set that combines a single-pione planetary gear and a double-pione planetary gear.
• the small-diameter first sun gear S2 of the planetary gear set 21 is detachably connected to the ring gear R1 of the deceleration planetary gear 20 by the first clutch C-1, and the large-diameter second sun gear S3 is connected to the third sun gear S3.
• the clutch C-3 is detachably connected to the ring gear R1 of the speed reduction planetary gear 20, and the fourth clutch C-4 is detachably connected to the input shaft 15 via the carrier C1 of the speed reduction planetary gear 20.
• the Short pion 25 is engaged with first sun gear S2.
• the long pinion 26 is mated with the second sun gear S3 and the short pinion 25. These short pion 25 and long pion 26 are rotatably supported by carriers C2 and C3 having a direct connection structure.
• the ring gear R2 is coupled to the long pinion 26 and is connected to the output shaft 16 as an output element.
• the second sun gear S3 is detachably connected to the transmission case 11 by the first brake B-1.
• the carrier C2 (C3) is detachably connected to the input shaft 15 by the second clutch C-2.
• the carrier C2 (C3) is detachably coupled to the transmission case 11 by the second brake B-2 and can be locked by the one-way clutch F-1.
• the automatic transmission 10 configured as described above selectively engages the first to fourth clutches C-1 to C-4 and the first and second brakes B-1 and B-2.
• a gear ratio of 8 forward speeds and 2 reverse speeds can be established. it can.
• Fig. 2 when the circles for the clutches and brakes corresponding to each gear stage are marked with ⁇ , the clutch and brake are engaged, and when there is no mark, the clutch is released.
• the shift range is P (parking) range and N (neutral) range
• all clutches C-1 to C-4 and brakes B1, B-2 are in the disengaged state, so input shaft 15 and output shaft Power transmission to 16 is disconnected.
• the first clutch C-1 is engaged and the one-way clutch F-1 is engaged.
• the reduction rotational force of the ring gear R1 of the speed reduction planetary gear 20 is input to the first sun gear S2 of the planetary gear set 21 via the first clutch C-1.
• the reduced rotational force of the first sun gear S2 is further decelerated via the carrier C2 (C3), whose rotation in one direction is restricted by the one-way clutch F-1, and input to the ring gear R2, and the output shaft 16 is in the first speed. It is decelerated at a gear ratio of
• the second brake B-2 is engaged in place of the one-way clutch F-1, and the rotation of the carrier C2 (C3) is fixed.
• the reduction rotational force of the ring gear R1 of the speed reduction planetary gear 20 is input to the first sun gear S2 via the first clutch C-1, and the rotation of the input shaft 15 is also transmitted via the second clutch C-2. Therefore, the ring gear R2 and the output shaft 16 are decelerated at a gear ratio of 5th speed and rotated forward.
• FIGS. 3 and 4 are mechanism diagrams showing specific configurations of the speed reduction planetary gear 20, the third and fourth clutches C-3 and C-4, and the first brake B-1.
• an input shaft 15 is rotatably supported by a transmission case 11, an oil pump body 27 fixed to the transmission case 11, and a stator shaft 30.
• the stator shaft 30 is press-fitted and fixed to the inner periphery of the boss portion 27a of the oil pump body 27.
• a speed reduction planetary gear 20 is disposed on the outer peripheral side of the rear end portion of the stator shaft 30, and the sun gear S1 of the speed reduction planetary gear 20 is made non-rotatable by spline engagement.
• a third clutch C-3 having a bottomed cylindrical first drum 31 and a fourth clutch C-4 having a bottomed cylindrical second drum 32 are accommodated.
• the fourth clutch C-4 is accommodated on the inner peripheral side of the first drum 31.
• the first drum 31 is rotatably supported on the outer periphery of the sleeve member 33 press-fitted on the outer periphery of the boss portion 27a of the oil pump body 27.
• the second drum 32 is supported by a box portion 3 la extending on the inner peripheral side of the first drum 31 and is engaged with a spline engaging portion 95 described later so as to be integrally rotatable. Yes.
• a plurality of seal members are interposed between the inner periphery of the boss portion 31 a of the first drum 31 and the outer periphery of the sleeve member 33.
• the rear end of the boss portion 31a of the first drum 31 is rotated by a main bearing 36 disposed on a fixed sleeve 35 fitted to the outer periphery of the rear end portion of the boss portion 27a of the oil pump body 27. Supported as possible.
• the main bearing 36 alone has a sufficient axial length to rotatably support the first drum 31.
• an auxiliary bearing 37 having a shorter axial length than the main bearing 36 is press-fitted into the inner periphery of the front end portion of the boss portion 31a.
• the auxiliary bearing 37 is loosely fitted on the outer periphery of the sleeve member 33 with a gap, and normally does not function as a bearing.
• the auxiliary bearing 37 functions as a bearing by contacting the outer periphery of the sleeve member 33 only when the first drum 31 is tilted by a predetermined amount or more in the axial direction.
• the third clutch C-3 is composed of a friction engagement element consisting of a separate plate 41 splined to the outer periphery 31b and a friction plate 42 splined to the ring gear R1, and a first hydraulic servo.
• the first hydraulic servo is a canceller disposed in a first piston 44 slidably housed in a first cylinder chamber 43 formed at the bottom of the first drum 31 and a boss 31a of the first drum 31.
• the plate 91 and a return spring 45 that urges the first piston 44 are configured.
• the inner peripheral portion of the canceller plate 91 is locked to the outer periphery of the boss portion 31a of the first drum 31 by a snap ring 90 so as to be restricted from moving in one axial direction.
• the outer peripheral portion is liquid-tightly fitted to the inner peripheral surface of the first piston 44, and a first cancel chamber 92 is formed between the canceller plate 91 and the first piston 44.
• a return spring 45 is disposed between the canceller plate 91 and the first piston 44 to urge the first piston 44 in the axial direction so as to release the third clutch C-3.
• the first cancel chamber 92 receives cancel oil (lubricating oil) from the boss portion 27a of the oil pump body 27, the sleeve member 33, and the cancel oil supply hole 93 formed in the radial direction in the first drum 31. It comes to be supplied.
• the cancel oil supplied to the first cancel chamber 92 is discharged to the outside through a cancel oil discharge groove 91a formed in the inner peripheral portion of the canceller plate 91.
• the first cancel chamber 92 has a function of canceling the centrifugal hydraulic pressure generated by the oil in the first cylinder chamber 43.
• the first piston 44 extends along the inner periphery of the outer peripheral portion 31b of the first drum 31, and the tip portion thereof is arranged corresponding to the side of the friction engagement element of the third clutch C3. ing.
• the first cylinder chamber 43 of the hydraulic servo is formed in the boss portion 27a of the oil pump body 27 through the supply passage 47 that also has oil holes formed in the sleeve member 33 and the boss portion 31a of the first drum 31. It is communicated with the oil passage that is formed.
• the oil passage formed in the boss part 27a is connected to a hydraulic control device (not shown), and the first piston 44 is slid by the spring force of the return spring 45 by the pressure oil supplied from the hydraulic control device.
• the friction engagement element of the third clutch C 3 is frictionally engaged.
• the second drum 32 is disposed inside the first piston 44 of the third clutch C-3.
• a boss portion 32a disposed on the boss portion 31a of the first drum 31 is provided on the inner peripheral side of the second drum 32, and an outer peripheral portion 32b is provided on the outer peripheral side.
• an inner spline 32c is formed on the inner periphery of the rear end of the boss portion 32a of the second drum 32.
• the inner spline 32c is formed in front of the boss portion 31a of the first drum 31.
• a spline engaging portion 95 is constituted by the first spline teeth composed of the outer splines 31c and the second spline teeth composed of the inner splines 32c.
• the opening side (rear side) end of the outer peripheral portion 32b of the second drum 32 is detachably connected to the carrier C1 of the speed reduction planetary gear 20 via the fourth clutch C-4. It has become.
• the fourth clutch C-4 includes a separate plate 51 spline-engaged on the inner periphery of the outer peripheral portion 32b and a flexion plate 52 spline-engaged on the outer periphery of the clutch hub 56 coupled to the carrier C1.
• the second hydraulic servo is a canceller disposed in a second piston 54 slidably housed in a second cylinder chamber 53 formed at the bottom of the second drum 32 and a boss 31a of the first drum 31.
• the plate 97 and the return spring 55 that urges the second piston 54 are configured.
• One end of the second piston 54 is spline-engaged with the inner periphery of the outer peripheral portion 32b of the second drum 32, and is disposed behind the friction engagement element of the fourth clutch C-4.
• the second piston 54 is disposed on the outer peripheral side of the boss portion 32a of the second drum 32 in which the spline engaging portion 95 is formed.
• a canceller plate 97 is disposed on the outer periphery of the rear end portion of the boss portion 31 a of the first drum 31 so as to be restricted from moving in one axial direction by a snap ring 96.
• the outer diameter side of the second piston 54 is fitted into the inner peripheral surface of the second piston 54, and a second cancel chamber 98 is formed between the canceller plate 97 and the second piston 54.
• a return spring 55 that urges the second piston 54 to open the fourth clutch C-4 in the axial direction.
• the second cylinder chamber 53 of the hydraulic servo has a pressure oil supply passage 60 formed between the boss portions 31a and 32a of the first and second drums 31 and 32, and an annular shape formed in the fixed sleeve 33. Via oil passages 61 and oil hole passages 62 formed in the bosses 27a of the oil pump body 27, respectively. Connected to a hydraulic control device (not shown)!
• the pressure oil supply passage 60 has a plurality of first oils formed in the boss portion 31a of the first drum 31 in the radial direction and formed at equal intervals in the circumferential direction.
• Holes 65, a plurality of second oil holes 66 formed in the boss portion 32a of the second drum 32 in the radial direction and formed at equal intervals in the circumferential direction, and both boss portions 31a, 32a is constituted by an annular oil passage 67 formed by a pair of seal rings, and the first and second oil holes 65, 66 are communicated with each other via the annular oil passage 67.
• the outer periphery of the outer peripheral portion 31b of the first drum 31 is detachably connected to the transmission case 11 via the first brake B-1.
• the first brake B-1 is a friction consisting of a separate plate 71 splined to the inner periphery of the mission case 11 and a friction plate 72 splined to the outer periphery of the outer periphery 3 lb of the first drum 31. It is composed of an engagement element and a hydraulic servo.
• the hydraulic servo is composed of a piston 74 slidably housed in a cylinder chamber 73 formed in the mission case 11 and a return spring 75 that urges the piston 74.
• the tip of the piston 74 extends to the side of the friction engagement element of the first brake B-1.
• the cylinder chamber 73 of the hydraulic servo is connected to the hydraulic control device via an unillustrated oil passage formed in the transmission case 11, and the piston 74 is connected to the return spring 75 by the pressure oil supplied from the hydraulic control device. It is slid against the spring force and frictionally engages the frictional engagement element of the first brake B-1. When the supply of pressure oil is stopped, the frictional engagement of the frictional engagement element is released by the spring force of the return spring 75.
• a lubrication supply passage 81 is formed in the input shaft 15, and lubricating oil discharged from an unillustrated oil pump is supplied to the supply passage 81 via the hydraulic control device and the supply hole 83. It has become so.
• a plurality of rows of supply holes 84, 85 are communicated with the supply passage 81, and the lubricating oil is supplied to each part in the transmission case 11 through these supply holes 84, 85.
• Lubricating oil supplied into the mission case 11 is scattered radially outward by centrifugal action and supplied to various parts such as the planetary gear 20 for reduction, the clutches C3 and C4, the brake B-1 and the bearings.
• first oil holes 65 on the circumference formed in the boss portion 31a of the first drum 31 and a circle on the circumference formed in the boss portion 32a of the second drum 32.
• the phase relationship with the plurality of second oil holes 66 is shown.
• the first oil hole 65 is indicated by a white circle and the second oil hole 66 is indicated by a black circle.
• six first oil holes 65 are formed at equal intervals on the circumference, and four second oil holes 66 are formed at equal intervals on the circumference.
• the second drum 32 is a force that is spline-engaged with the first drum 31 at an arbitrary angle phase when the second drum 32 is assembled.
• annular oil passage formed in the fixing ring 33 by a supply hole 63 formed in the input shaft 15 from an unillustrated hydraulic control device, an oil passage 62 formed in the boss portion 27a of the oil pump body 27, and the fixing ring 33.
• the pressure oil is distributed to six first oil passages 65 on the circumference via 61, and the pressure oil distributed to the first oil passage 65 is an annular oil formed on the inner periphery of the second drum 32.
• the oil is distributed to four second oil passages 66 on the circumference via the passage 67 and supplied to the second cylinder chamber 53 of the second hydraulic servo.
• the pressure oil that has passed through the first oil passage 65 can reach the second oil passage 66 only by flowing 0 1 (15 degrees) in the circumferential direction in the circumferential direction even at the maximum. Therefore, variation in the pressure oil supply path (supply length) can be reduced.
• the phase shift of the first and second oil holes 65 and 66 when the second drum 32 is arbitrarily assembled to the first drum 31 can be minimized.
• 4th clutch due to phase shift during assembly C-4 The hydraulic servo of hydraulic servo of 4 can be reduced in the oil supply path (supply length) 53, and friction due to phase shift during assembly.
• the variation in the engagement time of the engagement elements can be improved.
• first and second oil holes 65, 66 on the circumference are in phase with each other, and the hydraulic servo passes through the first and second oil holes 65, 66 in the two places. If pressure oil can be supplied to the second cylinder 54 of the cylinder, problems such as a response delay of the hydraulic servo will not occur. Therefore, the first and second oil holes 65 other than the two on the circumference 65 , Even if the phase shift of 66 is large, there is no particular problem.
• the number of the first and second oil holes 65, 66 is equal to four.
• a phase shift of up to 45 degrees occurs, and in the case of 6 pieces, up to 30 degrees. This causes a phase shift of. Therefore, the variation in the oil supply path (supply length) due to the phase shift at the time of assembly becomes large, and the engagement time of the friction engagement element varies.
• phase shift is greater when six first and second oil holes 65, 66 are used.
• the number of the first and second oil holes 65 and 66 is increased, the phase shift can be reduced.
• increasing the number of oil holes unnecessarily increases the processing cost.
• the strength of the drum decreases, so the drum thickness must be increased to compensate for the decrease in strength, and the overall weight increases. Therefore, it is important to reduce the phase shift between the first and second oil holes 65 and 66 without increasing the number of oil holes as much as possible.
• FIGS. 7 to 9 show other embodiments of the present invention, in which the combination of the first oil hole 65 and the second oil hole 66 is varied.
• the number of the first and second oil holes 65 and 66 is 8 and 4, respectively.
• the second drum 32 is replaced with the first drum 31.
• the phase difference ⁇ 2 of the first and second oil holes 65 and 66 can be made 22.5 degrees or less at least at two places on the circumference.
• the number (8) of the first oil holes 65 is a multiple of the second oil hole 66 (4), the phase force of the second oil hole 66 is equal to the two first oil holes 66. If the phase is set to the intermediate phase of the holes 65, the phases of all the second oil holes 66 are intermediate to the phases of the first oil holes 65, and the first oil holes shown in FIG.
• the force phase difference ⁇ in which the first oil holes are increased becomes larger. Therefore, it is more preferable that the relationship between the number of the first oil holes 65 and the number of the second oil holes 66 is not a multiple relationship.
• the combination shown in FIG. 8 is one in which the first and second oil holes 65, 66 are odd and even.
• the first oil holes 65 are arranged on the circumference or the like.
• An example is shown in which five angular intervals and four second oil holes 66 are arranged at equal angular intervals on the circumference.
• Sarasako the combination shown in Fig. 9 has an odd number of first and second oil holes 65 and 66, respectively. Specifically, the example shows five first oil holes 65 at equal circumferential intervals and three second oil holes 66 at equal circumferential intervals. .
• the fourth clutch C— is provided via the first oil hole 65 formed in the first drum 31 and the second oil hole 66 formed in the second drum 32.
• a plurality of first and second oil holes 65, 66 are different from each other, for example, six first oil holes formed at equal angular intervals on the circumference. 65 and four second oil holes 66 formed at equal angular intervals on the circumference, the first drum when the second drum 32 is arbitrarily threaded onto the first drum 31.
• the phase shift of the second oil holes 65 and 66 can be minimized.
• the number of the first and second oil holes 65 and 66 may be a combination of multiples such as 8 and 4, or odd and even numbers such as 5 and 4. Even if the number of the first and second oil holes 65 and 66 is the same, the number of the first and second oil holes 65 and 66 is the same. This makes it possible to reduce variations in the oil supply path (supply length) to the second cylinder chamber 54 of the hydraulic servo of the fourth clutch C-4 due to the phase shift during assembly.
• the present invention is not limited to such an example. It can be applied to a wide range of automatic transmissions that supply pressure oil between two drums.
• the planetary gear set 21 is described as an example of a rabbi type gear set in which the single pinion planetary gear and the double beon planetary gear are combined.
• the planetary gear set 21 in the present invention is Any planetary gear set having a plurality of (two or more) planetary gears is not limited to the rabbi gear set, and any configuration can be adopted.
• stator shaft 30, the oil pump body 27, the sleeve member 33, and the like are integrally coupled to the transmission case 11, the stator shaft 30, the oil pump body 27, the sleeve member 33, and the like are connected to the mission case 11. It forms part of Case 11.
• the pressure oil supply device in the automatic transmission according to the present invention is suitable for use in an automatic transmission having a speed change mechanism that disengages and disengages a plurality of clutches and brakes into a plurality of stages.

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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)
• Structure Of Transmissions (AREA)
• General Details Of Gearings (AREA)

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• 2005
  • 2005-11-17 JP JP2005333338A patent/JP4906045B2/ja not_active Expired - Fee Related
• 2006
  • 2006-10-06 DE DE112006002240T patent/DE112006002240B8/de not_active Expired - Fee Related
  • 2006-10-06 CN CN200680031175.2A patent/CN101248293B/zh not_active Expired - Fee Related
  • 2006-10-06 WO PCT/JP2006/320063 patent/WO2007058028A1/ja active Application Filing

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