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
  • 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
  • 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
• • 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
  • F16D65/00—Parts or details
  • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
  • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
  • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
  • F16D65/186—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes with full-face force-applying member, e.g. annular
• • 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
  • F16D2121/00—Type of actuator operation force
  • F16D2121/02—Fluid pressure
• • 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
  • F16D2125/00—Components of actuators
  • F16D2125/02—Fluid-pressure mechanisms
  • F16D2125/06—Pistons
• • 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
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T29/00—Metal working
  • Y10T29/53—Means to assemble or disassemble

Definitions

• the present invention relates to a piston provided in an automatic transmission, and more particularly to a screw manufactured by press processing.
• a piston manufactured by press processing is known as a screw that is provided in an automatic transmission to operate a clutch, a brake, etc., in order to reduce manufacturing cost and to make the mounting space compact.
• a screw that is provided in an automatic transmission to operate a clutch, a brake, etc.
• Patent Document 1 Japanese Patent Application Laid-Open No. 11 938 30 0
• Patent Document 2 Japanese Patent Application Laid-Open No. 2 0 0 2 0 2 5 5 6 4
• the piston described in Patent Document 1 includes a cylindrical portion and a bottom portion provided on one end side of the cylindrical portion. The bottom portion constitutes a part of the wall of the hydraulic chamber, and a flange portion is formed at the other end (tip) of the cylindrical portion.
• the flange portion at the tip of the cylindrical portion presses the clutch plate.
• Such pistons are manufactured by sheet metal presses and are therefore low cost.
• the bottom part that forms a part of the wall of the hydraulic chamber and the tip (flange part) of the cylindrical part that presses the friction plate can be arranged in different spaces, so the narrow space can be effectively used.
• the present invention has been made against the background described above, and its object is to provide a press-made automatic transmission biston having a detent structure and capable of being manufactured at low cost. It is. Disclosure of the invention
• a first invention for achieving the above object is a piston for an automatic transmission made of a press, comprising: a cylindrical portion; and a bottom portion provided on one end side of the cylindrical portion; A part of the cylindrical portion is formed by being cut and raised in the radial direction, and is characterized by including a claw piece engaged with a predetermined non-rotating member.
• the claw piece functioning as the detent structure is formed by cutting and raising a part of the cylindrical portion, the screw screw is formed for the claw piece. Since it is not necessary to increase the size of the raw material, even if it has a detent structure, bisone can be manufactured at low cost.
• the second invention is characterized in that it is driven in the axial direction in order to press a friction plate provided between the piston force rotary member of the first invention and the non-rotation member. .
• the friction plate is engaged by the piston whose rotation about the axial center is blocked by the claw piece.
• a part of the cylindrical part of the screw can be cut in the circumferential direction. It is characterized in that a notched notch is provided, and in the notch, a rotating member that rotates around another axis parallel to the axis of the piston is disposed. As a result, interference between the piston and the rotating member, which is prevented from rotating about the axis by the claws, is prevented.
• a fourth aspect of the invention is characterized in that the non-rotational member is disposed on the rotational direction side of the claw piece at the time of operation of the friction plate. In this way, the necessary and sufficient detent structure is obtained, and the structure is simplified.
• the non-rotational member has an engagement protrusion having an engagement surface parallel to the axis of the screw, and the claw piece is brought into contact with the engagement surface. It is characterized in that it allows movement of the piston in the axial direction. In this way, the axial movement of biston is permitted while the detent of the biston is covered.
• FIG. 1 is a cross-sectional view showing a part of a vehicular automatic transmission provided with a screw according to an embodiment of the present invention.
• FIG. 2 is a cross-sectional view of a main part of FIG. Explanation of sign
• FIG. 1 is a cross-sectional view showing a part of an automatic transmission 10 for a vehicle provided with a biston 26 according to one embodiment of the present invention, that is, an upper half of an axial center C1 represented by a one-dot chain line.
• the automatic transmission 10 shown in FIG. 1 includes a housing case 12 which is a non-rotating member, and a compensator drive gear provided in the housing case 12 and made rotatable relative to the input shaft 14. It has 16 and.
• the counter drive gear 16 is provided on a cylindrical shaft 18 parallel to the input shaft 14 and at one axial end of the shaft 18 and is substantially perpendicular to the cylindrical shaft 18.
• the gear part 20 projects outward.
• the input shaft 14 and the counter drive gear 16 have a common axis C 1.
• the housing case 11 is formed with a support wall 22 projecting toward the cylindrical shaft 18 of the counter drive gear 16 at a position adjacent to the gear 10 of the force drive gear 16.
• the cylindrical shaft 18 is rotatably supported by the support wall 22 via a bearing 24 provided on the outer peripheral side of the cylindrical shaft 18.
• a piston 26 having a common axis C 1 is disposed radially outward of the counter drive gear 16.
• the biston 26 is a press-formed product bent from a single metal plate such as a steel plate using a press die, and is an outer periphery positioned outside the gear portion 20 of the counter drive gear 16 in the radial direction.
• a tube portion 28 which is a wall, a bottom portion 30 which is a bottom wall provided at one end of the support wall 22 side of the tube portion 2 8, and a brake 44 which will be described later at the other end of the tube portion 28.
• a flange portion 32 provided for pressing and bent radially outward substantially perpendicularly to the cylindrical portion 28.
• the bottom 30 is It is an inward flange shape which protrudes substantially inward and radially inward with respect to the cylindrical portion 28 and is positioned on the support wall 22 side in the axial center direction from the outer peripheral portion 3 0 a and the outer peripheral portion 3 0 a And an inner circumferential portion 3 O b formed as described above.
• the inner periphery 30 b of the bottom 30 is slidably fitted in an annular recess 34 formed on the side surface of the support wall 22 on the counter drive gear 16 side.
• the surface of the bottom portion 30 on the side facing the support wall 22 of the inner circumferential portion 3 O b is oil-tightly sealed between the radial direction both ends of the inner circumferential portion 3 0 b and the support wall 22.
• a rubber member 36 for bonding is attached, and an oil chamber 38 is formed between the annular recess 34 and the rubber member 36.
• a dish-shaped return spring 40 for biasing the bottom 30 of the piston 26 toward the oil chamber 38 on the opening side of the bottom 30 of the bistone 26 is provided in the annular recess 34. It is housed.
• the outer peripheral end of the disc-shaped return spring 40 is in contact with the outer peripheral portion 3 0 a of the bottom 30 of the piston 2 6, and the inner peripheral end of the disc-shaped return spring 40 A disc-shaped return spring 40 is abutted on a snap ring 42 fitted on a support wall 22 in order to inhibit the movement of the counter drive gear 16 to the side.
• a brake 44 that functions as a frictional engagement element for suppressing the rotation of the ring gear 48 is disposed at a position facing the flange portion 32 of the piston 26 in the housing case 12.
• the brake 44 is alternately interposed between a plurality of inward friction plates 46 and a plurality of inward friction plates 46 which are spline-fit relative to each other on the inner circumferential side of the case 12 so as not to be relatively rotatable.
• it is composed of a plurality of outwardly directed friction plates 50 spline-fitted non-rotatably to the outer peripheral surface of the ring gear 4 8.
• a part of cylindrical part 28 is cut and raised radially outward by press processing, thereby corresponding to claw piece 52 that functions as a detent device and its claw piece 52. And a through hole 54 which is a portion to be formed.
• the claw piece 52 is, for example, in the form of a band having a predetermined width and a predetermined length, and the outer peripheral surface of the cylindrical portion 28 and the inner wall surface of the housing case 12 so as not to contact the inner wall surface of the housing case 12. The height of the dimension is shorter than the dimension between.
• a protrusion 56 for engagement is integrally projected from the housing case 12.
• the protrusion 56 also corresponds to the non-rotating member together with the housing case 11.
• the projection 56 is provided with an engagement surface 5 6 a for engaging with the claw piece 5.
• the engaging surface 56a is a plane formed parallel to the axial center C1 and allows movement of the bistone 26 in a direction parallel to the axial center C1.
• the through hole 54 functions as a hole for removing oil, and the lubricating oil in the piston 26 is made to flow radially outward from the through hole 54, so that the counter drive gear 16 rotates. Since the amount of the lubricating oil in the piston 26 during rotation, that is, the amount of agitation of the lubricating oil decreases, the loss due to the agitation decreases. In addition, when the discharge amount of the lubricating oil is insufficient only with the through hole 54, even if one or more oil drain holes are further formed by punching out a part of the cylindrical portion 28. Good.
• FIG. 2 is a cross-sectional view of an essential part of 11 H in FIG. As shown in FIG.
• the cylindrical portion 2 8 of the piston 2 6 is formed so as to cover most of the counter drive gear 16 from the outside.
• a notch 60 is provided by removing a portion corresponding to about 90 ° of the axis, and provided within the notch 60 so as to be rotatable around another axis C 2 parallel to the axis C 1.
• the bistone 2 is moved. Since the flange portion 32 of 6 presses the inward friction plate 46, the inward friction plate 46 and the outward friction plate 50 are engaged, and the rotation of the outward friction plate 50 is stopped. At this time, due to a slight circumferential clearance between the case 11 and the inward friction plate 46, the inward friction plate 46 is rotated by the clearance. Therefore, a force is also applied to the piston 26 pressing the inward friction plate 46 in the rotational direction, but as described above, the claw piece 52 formed on the piston 26 engages with the protrusion 56 Because there are Rotation is blocked.
• the claw portion 52 functioning as a rotation stopping device for the biston 26 is formed by cutting and raising a part of the cylindrical portion 28 within the press forming process.
• the bistone 26 can be manufactured at low cost even with the detent structure.
• the inward friction plate 46 and the outward friction of the brake 4 4 provided between the counter drive gear 16 corresponding to the rotating member and the housing case 12 corresponding to the non-rotating member Since it is driven in the direction of the axis C 1 to press the plate 50, the brake 4 4 is engaged and actuated by a screw whose rotation around the axis C 1 is blocked by the claw piece 52. Ru.
• the biston 26 is provided with the notch 60 in which a part of the cylindrical portion 28 of the piston 26 is cut away in the circumferential direction. Since the counter driven gear 58 corresponding to a rotating member rotating around another axis C parallel to the axis C 1 of the piston 2 6 is disposed, Interference between the piston 26 whose rotation around the center C 1 is blocked and the counter driven gear 58 is prevented.
• the housing case 12 corresponding to the non-rotating member and the brake 44 on the claw piece 52 are disposed in the rotational direction at the time of engagement operation, it is necessary. And, it has a sufficient detent structure, and the structure of detent device of piston 26 becomes simple.
• the housing case 12 corresponding to the non-rotating member has the engagement projection 56 having the engagement surface 5 6 a parallel to the axial center C 1 of the piston 2 6.
• the claw piece 52 is brought into contact with the engagement surface 56a of the claw piece 52 so as to allow the movement of the screw core 26 in the axial center C1 direction. While the movement of the piston is permitted, the rotation of the piston 26 is carried out.
• the claw piece 52 was cut and raised radially outward and engaged with the projection 56 provided on the non-rotational housing case 12.
• the claw piece may be cut and raised radially inward, and the non-rotating member may be provided with an engaging portion to be engaged with the claw piece.
• the protrusion 56 is integrally formed from the housing case 12 so as to engage with the claw piece 52 in the rotation direction of the outward friction plate 50 when the brake 4 4 is actuated. Although it was provided in a protruding manner, it may be provided so as to engage with the claw piece 52 in both the rotational direction side and the counter-rotational direction side of the outward friction plate 50. Further, the protrusion 56 may be integrally formed with the housing case 12 or may be formed of a separate part fixed to the inner wall surface of the housing case 12.
• the part disposed in the notch 60 of the cylinder part 18 of the biston 26 is the counter drive gear 16, but the part disposed in the notch portion is It may be any part.
• the counterbalance drive gear 28 is disposed in the notch 60 formed in the cylindrical portion 28, it is necessary to prohibit the rotation of the piston 26.
• the reason for prohibiting the rotation of 2 6 is not limited to that of the above embodiment.
• the present invention is applicable to a press-made piston requiring a detent structure regardless of the reason for requiring the detent structure.
• the claw pieces 52 may be provided at a plurality of forces provided only at one place. Further, the shape of the claw piece 52 is not limited to a belt shape.
• the piston 26 is slidably fitted in the annular recess 34 provided in the housing case 12 which is a non-rotating member. It may be slidably fitted in an annular recess formed in a member that does not rotate relative to the shaft.
• the non-rotating member means a member that does not rotate relative to the piston 26.

Landscapes

• 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)
• Gear-Shifting Mechanisms (AREA)
• Braking Arrangements (AREA)

Priority Applications (1)

Applications Claiming Priority (2)

Publications (1)

Family

ID=35394242

Family Applications (1)

Country Status (4)

Cited By (1)

Families Citing this family (5)

Citations (4)

Family Cites Families (10)

• 2004
  • 2004-05-14 JP JP2004145276A patent/JP2005325937A/ja active Pending
• 2005
  • 2005-05-13 US US11/568,844 patent/US20070256294A1/en not_active Abandoned
  • 2005-05-13 CN CNA2005800153542A patent/CN1954163A/zh active Pending
  • 2005-05-13 WO PCT/JP2005/009207 patent/WO2005111477A1/ja not_active Ceased

Patent Citations (4)

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