JP5373466B2 - Oil passage structure of continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide the oil passage structure for a continuously variable transmission, reducing concentration of stress to an oil passage of a boss part of a piston. <P>SOLUTION: A fitting part 118 fitted in an output shaft 48 is provided with an oil passage 116, and an end surface 120 corresponding the oil passage 116 is provided with a recess 122. The output shaft 48 is positioned in the continuously variable transmission 16 by a nut 124 through a driven side bearing 53, and a driven side piston 108 is fixed to the output shaft 48, with the end surface 120 made adjacent to the driven side bearing 53. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to an oil passage structure of a continuously variable transmission provided with a centrifugal hydraulic pressure canceling chamber so as to cancel centrifugal hydraulic pressure generated in a hydraulic chamber of a pulley.

  Conventionally, the following is known as an oil passage structure of the continuously variable transmission (see Patent Document 1).

   A pulley comprising a fixed pulley member fixed to the rotating shaft and a movable pulley member mounted on the rotating shaft so as to be axially movable and non-rotatable is provided. A cylinder projects from the outer peripheral edge of the movable pulley member toward the back side of the movable pulley member. The rotary shaft is provided with a piston that forms an oil pressure chamber on the back side of the movable pulley member so that the outer peripheral surface is slidably in close contact with the inner peripheral surface of the cylinder. A centrifugal hydraulic pressure cancellation chamber is provided in which oil is supplied on the outer surface side of the piston. The cylinder is provided with a cancel chamber wall that cooperates with the outer surface of the piston to form part of the centrifugal hydraulic pressure cancel chamber. The rotation shaft is provided with a spacer on the outer surface side of the piston. The spacer is provided with an oil guide body that cooperates with the outer surface of the piston to form the other part of the centrifugal hydraulic pressure canceling chamber.

JP 2000-249205 A

  However, in the above prior art, when forming the oil passage structure of the continuously variable transmission, a spacer is provided on the rotating shaft on the outer surface side of the piston, and the oil passage structure is formed in this spacer.

  Therefore, it is conceivable to provide an oil passage in the boss portion of the piston in order to omit this spacer.

  However, the boss portion of the piston has a return spring that is provided in the hydraulic chamber for driving and holding the belt of the continuously variable transmission, a return spring that is provided in the hydraulic chamber and is biased in the axial direction of the rotary shaft. Since the load and the load of the nut attached so that the rotating shaft is positioned and supported by the continuously variable transmission main body through the bearing are applied, the stress is concentrated in the oil passage.

  An object of the present invention is to provide an oil passage structure of a continuously variable transmission that can reduce the concentration of stress in an oil passage of a boss portion of a piston.

The present invention relates to a pulley comprising a fixed pulley member fixed to a rotating shaft and a movable pulley member that is movable in the axial direction of the rotating shaft and immovable in the rotating direction of the rotating shaft, and the movable pulley member A cylinder that is provided at an outer peripheral edge of the movable pulley member and protrudes toward the back side of the movable pulley member, and an outer peripheral surface that slides on an inner peripheral surface of the cylinder on the rear side of the movable pulley member that is provided on the rotating shaft. A piston that forms a hydraulic chamber in close contact with each other, a centrifugal hydraulic pressure cancellation chamber that is supplied with oil on the outer surface side of the piston, and an oil passage that is formed on the rotating shaft and guides oil to the centrifugal hydraulic pressure cancellation chamber In the oil passage structure of the continuously variable transmission provided,
The rotating shaft is positioned and supported by a case with a nut via a bearing,
The piston is fixed to the rotating shaft with its outer end surface adjacent to the bearing,
The oil passage is formed in a fitting portion fitted to the rotating shaft of the piston,
A concave portion is formed on the outer end surface of the piston at a position corresponding to the oil passage in the radial direction of the rotating shaft .

According to the oil passage structure of the continuously variable transmission of the present invention, the oil passage is formed in the fitting portion that is fitted to the rotation shaft of the piston, and the oil passage in the radial direction of the rotation shaft on the outer end surface of the piston. Since the concave portion is formed at a position corresponding to, the concentration of stress in the oil passage of the fitting portion of the piston can be reduced.

In the oil passage structure of the present invention, the rotary shaft is positioned and supported by the case with a nut via a bearing, and the piston is fixed to the rotary shaft with its outer end face adjacent to the bearing.

Therefore, hydraulic pressure generated in the hydraulic chamber for driving and holding the belt of the continuously variable transmission, the load of the return spring is biased hydraulic chamber provided in the hydraulic chamber in the axial direction of the rotary shaft, and the rotation axis It is possible to reduce the concentration of stress in the oil passage of the fitting portion of the piston due to the load of the nut attached so as to be positioned and supported by the continuously variable transmission via the bearing.

1 is a schematic configuration diagram of a vehicle power transmission device to which an oil passage structure of a continuously variable reduction gear according to the present invention is applied. It is sectional drawing by the side of the driven of the vehicle power transmission device of FIG. It is a figure which shows the driven side piston of FIG. 2, (a) is a perspective view which shows a driven side piston, (b) is a figure which shows the recessed part of the end surface of a driven side piston.

  FIG. 1 shows a vehicle power transmission device 10 to which an oil passage structure of a continuously variable transmission according to the present invention is applied. The vehicle power transmission device 10 includes a continuously variable transmission (hereinafter referred to as CVT (Continuously Variable Transmission)) 16 that continuously changes the rotational speed of the output shaft 12a of the engine 12 in the vehicle and transmits the rotational speed to the wheel shaft 14. . The vehicle power transmission device 10 arbitrarily performs 2WD (2 Wheel Drive) driving using the front wheel 64 as a driving wheel and the rear wheel 65 as a driven wheel, and 4WD driving using both the front wheel 64 and the rear wheel 65 as driving wheels. It can be applied to vehicles that can be switched to.

  The vehicle power transmission device 10 is connected to a main controller 20 that controls the engine 12 in accordance with an instruction from the driver of the vehicle, a CVT control unit 22 that controls the transmission ratio of the CVT 16, and the main controller 20 and the CVT control unit 22. Various sensors (to be described later).

  A throttle valve 28 is disposed in the intake pipe 26 connected to the engine 12, and the throttle valve 28 controls the main controller 20 and the vacuum valve 30 in conjunction with the operation of an accelerator pedal (not shown) in the driver's seat. Open and close down.

  The output shaft 12 a of the engine 12 is connected to the torque converter 32. In the torque converter 32, the torque converter cover 32a connected to the output shaft 12a rotates the pump impeller 32b and rotates the turbine impeller 32c with respect to the torque converter shaft 34 through oil filled therein. At this time, the transmission torque can be increased by the action of the stator 32d. Further, in the torque converter 32, the rotation of the output shaft 12a can be directly transmitted to the torque converter shaft 34 by engaging the torque converter cover 32a and the torque converter shaft 34 by the lock-up clutch 32e.

  The torque converter shaft 34 is connected to a planetary gear type forward / reverse switching mechanism 36 of the CVT 16. The planetary gear type forward / reverse switching mechanism 36 includes an input rotation unit 36a that is integrally connected to the torque converter shaft 34, a forward clutch 36b that connects the input rotation unit 36a and the input shaft 38 of the CVT 16, and an input rotation unit. 36a and a ring gear 36c integrally formed. The planetary gear type forward / reverse switching mechanism 36 includes a sun gear 36d provided on the input shaft 38 and a plurality of planetary gears 36e meshing with the ring gear 36c, a carrier 36f for rotating and supporting the planetary gear 36e, and the carrier A reverse clutch 36g that engages the outer periphery of 36f with the housing.

  In the planetary gear type forward / reverse switching mechanism 36, the input rotating portion 36a and the input shaft 38 are integrally rotated in the same direction by engaging the input rotating portion 36a and the input shaft 38 by the forward clutch 36b. Can do. Further, by releasing the forward clutch 36b and engaging the carrier 36f and the housing by the reverse clutch 36g, the carrier 36f is fixed, and the input shaft 38 can be driven via the planetary gear 36e. In this case, the input shaft 38 rotates in the opposite direction to the rotation of the input rotating portion 36a, and the vehicle can be moved backward.

  The CVT 16 is driven to rotate by the planetary gear type forward / reverse switching mechanism 36, a drive pulley 40 (drive pulley) supported by the input shaft 38, and a metal belt 42 with respect to the rotation of the drive pulley 40. It has a driven pulley 44 (driven pulley) and an output shaft 48 that transmits the rotation of the driven pulley 44 to the intermediate shaft 46. The metal belt 42 is configured, for example, by attaching a large number of push pieces to two straps.

  The drive pulley 40 includes a fixed pulley member 40a fixed to the input shaft 38, and a movable pulley member 40b slidable in the axial direction by hydraulic pressure acting on a hydraulic oil chamber (hydraulic chamber) 50. The movable pulley member 40b The groove width of the groove 40c of the drive pulley 40 can be changed depending on the sliding position.

  Similarly, the driven pulley 44 includes a fixed pulley member 44a fixed to the output shaft 48 and a movable pulley member 44b slidable in the axial direction by the hydraulic pressure acting on the hydraulic oil chamber 52. The groove width of the groove 44c of the driven pulley 44 can be changed depending on the sliding position.

  The hydraulic oil supplied to the hydraulic oil chamber 50 is supplied from the pump 54 via the control valve 56 and the oil passage 38 a passing through the axial center of the input shaft 38, and is similarly supplied to the hydraulic oil chamber 52. Is supplied from the pump 54 through an oil passage 48 a that passes through the axial center of the control valve 58 and the output shaft 48. The control valves 56 and 58 operate under the control of the CVT control unit 22 and can change the pressure of the hydraulic oil chambers 50 and 52. Thereby, the movable pulley members 40b and 44b can be slid in the axial direction in conjunction with each other, and the widths of the grooves 40c and 44c can be continuously changed. Therefore, the ratio of the diameter around which the metal belt 42 is wound, that is, the transmission ratio can be changed steplessly. In FIG. 1, the drive pulley 40 and the driven pulley 44 schematically show an OD (Over Drive) state in which the upper half centered on each axis and a low state in the lower half centered on each axis. ing.

  The rotational speed of the input shaft 38 is steplessly changed by the CVT 16 and transmitted to the output shaft 48. The rotational speed of the output shaft 48 is decelerated by the intermediate shaft 46 and transmitted to the differential gear 60.

  The differential gear 60 can travel by driving the wheel shaft 14 and the front wheel 64 via a gear mechanism 60a for absorbing the difference in rotational speed between the inner wheel and the outer wheel during curve traveling.

  Connected to the main controller 20 are a throttle opening sensor 70 that detects a throttle opening TH that is the opening of the throttle valve 28, and a pressure sensor 72 that detects an absolute pressure PB downstream of the throttle valve 28. The main controller 20 includes a crank angle sensor 74 that detects the crank angle of the engine 12, a water temperature sensor 76 that detects the engine water temperature, an engine speed sensor 78 that detects the engine speed Ne, and a torque converter shaft 34. A torque converter rotational speed sensor 80 for detecting the rotational speed, front wheel speed sensors 82a and 82b for detecting the rotational speed Vf of the left and right front wheels 64, and a rear wheel speed sensor 83a for detecting the rotational speed Vr of the left and right rear wheels 65. , 83b.

  The CVT control unit 22 includes a pulley rotational speed sensor 81 that detects the rotational speed of the input shaft 38 by teeth provided on the outer peripheral portion of the fixed pulley member 40a, and an output by teeth provided on the outer peripheral portion of the fixed pulley member 44a. A pulley rotation speed sensor 84 that detects the rotation speed of the shaft 48 and a position switch 86 that outputs a signal indicating a shift range (D, N, P, etc.) selected by the driver are connected. The CVT control unit 22 includes a throttle opening sensor 70, a pressure sensor 72, a crank angle sensor 74, an engine speed sensor 78, a torque converter speed sensor 80, front wheel speed sensors 82a and 82b, and a rear wheel speed sensor 83a. , 83b are connected. Further, the main controller 20 and the CVT control unit 22 are connected by a communication line 88 and can communicate with each other such as data.

  In the drive pulley 40, a fixed pulley member 40a fixed to the input shaft 38 rotatably supported by the drive side bearing 41, and a movable pulley member 40b mounted on the input shaft 38 so as to be axially movable and non-rotatable. And are provided. A drive-side cylinder 102 projects from the outer peripheral edge of the movable pulley member 40b toward the back side of the movable pulley member 40b. In addition, the input shaft 38 is provided with a drive-side piston 104 that forms the hydraulic oil chamber 50 by slidably adhering the outer peripheral surface of the drive-side cylinder 102 to the inner peripheral surface on the back side of the movable pulley member 40b. Yes.

  In the driven pulley 44, as shown in FIG. 2, a fixed pulley member 44a fixed to the output shaft 48 rotatably supported by the driven-side bearing 53, and axially movable and non-rotatable on the output shaft 48. And a movable pulley member 44b attached to the. A driven cylinder 106 projects from the outer peripheral edge portion of the movable pulley member 44b toward the back side of the movable pulley member 44b. Further, the output shaft 48 is provided with a driven-side piston 108 that forms a hydraulic oil chamber 52 in such a manner that its outer peripheral surface is slidably in close contact with the inner peripheral surface of the driven-side cylinder 106 on the back side of the movable pulley member 44b. Yes. Further, a return spring 109 is provided between the driven piston 108 and the movable pulley member 44b.

  In the driven pulley 44, as shown in FIG. 2, the driven cylinder 106 is formed with a centrifugal hydraulic pressure cancel chamber 110 that cancels the hydraulic pressure of the hydraulic oil chamber 52 outside the driven piston 108. A cancellation chamber wall 112 that forms a part of the outside of the centrifugal hydraulic pressure cancellation chamber 110 in cooperation with the centrifugal hydraulic pressure cancellation chamber 110 is fixedly provided. The output shaft 48 is formed with an oil groove 114 communicating with the driven-side piston 108, and the driven-side piston 108 is formed with an oil passage 116 communicating with the centrifugal hydraulic pressure canceling chamber 110. And oil flows between the centrifugal oil pressure cancellation chamber 110.

As shown in FIGS. 2 and 3, the oil passage 116 is formed in a fitting portion 118 that is fitted to the output shaft 48 of the driven-side piston 108, and protrudes along the output shaft 48 that is a rotating shaft . A recess 122 is formed on the outer end surface 120 at a position corresponding to the oil passage 116 in the radial direction of the output shaft 48 .

Output shaft 48 is positioned and supported on the case at the nut 124 via the driven-side bearing (bearing) 53, driven-side piston 108 is fixed to the output shaft 48 to be adjacent the end surface 120 on the driven side bearing 53.

  The driven piston 108 is press-fitted with an oil guide body 126 that cooperates with the outer surface of the driven piston 108 to form another part inside the centrifugal hydraulic pressure canceling chamber 110. The oil guide body 126 is disposed so as to surround the oil passage 116 of the driven piston 108.

As described above, in the present embodiment, the output shaft 48 is positioned in the case of the continuously variable transmission 16 by the nut 124 via the driven-side bearing 53, and the driven-side piston 108 drives the outer end surface 120 thereof. It is fixed to the output shaft 48 adjacent to the side bearing 53. An oil passage 116 is formed in the fitting portion 118 of the piston 108 fitted to the output shaft 48, and a concave portion is formed in the outer end surface 120 of the piston 108 at a position corresponding to the oil passage 116 in the radial direction of the output shaft 48. 122 is formed.
According to this configuration, the hydraulic pressure generated in the hydraulic oil chamber 52 for driving and holding the metal belt 42 of the vehicle power transmission device 10, the piston 108 provided in the hydraulic oil chamber 52 is attached in the axial direction of the output shaft 48. The driven piston 108 is driven by the biasing force of the return spring 110 that is biased and the tightening force of the nut 124 that is attached so that the output shaft 48 is positioned and supported by the case of the continuously variable reduction gear 16 via the driven bearing 53. It is possible to reduce stress concentration in the oil passage 116 of the boss portion.

  DESCRIPTION OF SYMBOLS 10 ... Vehicle power transmission device, 12 ... Engine, 12a ... Output shaft, 14 ... Wheel shaft, 16 ... Continuously variable transmission, 20 ... Main controller, 22 ... CVT control part, 26 ... Intake pipe, 28 ... Throttle valve, 30 ... Vacuum valve, 32 ... Torque converter, 32a ... Torcon cover, 32b ... Pump impeller, 32c ... Turbine impeller, 32d ... Stator, 32e ... Lock-up clutch, 34 ... Torcon shaft, 36 ... Planetary gear type forward / reverse switching mechanism, 36a ... input rotating part, 36b ... forward clutch, 36c ... ring gear, 36d ... sun gear, 36e ... planetary gear, 36f ... carrier, 36g ... reverse clutch, 38 ... input shaft, 38a ... oil path, 40 ... drive pulley, 40a ... fixed pulley member, 40b ... movable pulley member, 42 ... metal belt, 4 ... driven pulley, 44a ... fixed pulley member, 44b ... movable pulley member, 46 ... intermediate shaft, 48 ... output shaft, 48a oil passage, 50 ... hydraulic oil chamber, 52 ... hydraulic oil chamber, 54 ... pump, 56 ... control Valve, 58 ... Control valve, 60 ... Differential, 60a ... Gear mechanism, 64 ... Front wheel, 65 ... Rear wheel, 70 ... Throttle opening sensor, 72 ... Pressure sensor, 74 ... Crank angle sensor, 76 ... Water temperature sensor, 78 ... Engine speed sensor, 80 ... Torcon speed sensor, 82a, 82b ... Front wheel speed sensor, 83a, 83b ... Rear wheel speed sensor, 88 ... Communication line, 102 ... Drive side cylinder, 104 ... Drive side piston, 106 ... Driven side cylinder, 108 ... Driven side piston, 109 ... Return spring, 110 ... Centrifugal oil pressure cancellation chamber, 12 ... cancel chamber wall, 114 ... oil groove 116 ... Oil passage 118 ... fitting portion 120 ... end face, 122 ... recessed portion, 124 ... nut 126 ... oil guide member.

Claims (1)

A pulley comprising a fixed pulley member fixed to a rotating shaft and a movable pulley member that is movable in the axial direction of the rotating shaft and immovable in the rotating direction of the rotating shaft;
A cylinder provided at an outer peripheral edge of the movable pulley member and projecting toward the back side of the movable pulley member;
A piston that is provided on the rotating shaft and has an outer peripheral surface slidably in close contact with the inner peripheral surface of the cylinder on the back side of the movable pulley member;
A centrifugal hydraulic pressure cancellation chamber to which oil is supplied on the outer surface side of the piston;
In an oil passage structure of a continuously variable transmission, comprising an oil passage formed on the rotary shaft and guiding oil to the centrifugal hydraulic pressure cancellation chamber,
The rotating shaft is positioned and supported by a case with a nut via a bearing,
The piston is fixed to the rotating shaft with its outer end surface adjacent to the bearing,
The oil passage is formed in a fitting portion fitted to the rotating shaft of the piston,
An oil passage structure for a continuously variable transmission, wherein a recess is formed at a position corresponding to the oil passage in the radial direction of the rotary shaft on the outer end surface of the piston.