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WO1999000199A1 - Embrayage couplable sous charge et son procede de realisation - Google Patents

Embrayage couplable sous charge et son procede de realisation Download PDF

Info

Publication number
WO1999000199A1
WO1999000199A1 PCT/US1997/011266 US9711266W WO9900199A1 WO 1999000199 A1 WO1999000199 A1 WO 1999000199A1 US 9711266 W US9711266 W US 9711266W WO 9900199 A1 WO9900199 A1 WO 9900199A1
Authority
WO
WIPO (PCT)
Prior art keywords
drum
clutch
large diameter
wall
backing plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US1997/011266
Other languages
English (en)
Inventor
Bruce A. Skaggs
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Rockford Powertrain Inc
Original Assignee
Rockford Powertrain Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Rockford Powertrain Inc filed Critical Rockford Powertrain Inc
Priority to PCT/US1997/011266 priority Critical patent/WO1999000199A1/fr
Publication of WO1999000199A1 publication Critical patent/WO1999000199A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D15/00—Corrugating tubes
    • B21D15/02—Corrugating tubes longitudinally
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/26—Making other particular articles wheels or the like
    • B21D53/28—Making other particular articles wheels or the like gear wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/648—Clutch-plates; Clutch-lamellae for clutches with 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
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • F16D2250/00—Manufacturing; Assembly
    • F16D2250/0023—Shaping by pressure

Definitions

  • the present invention generally relates to clutches, and more particularly relates to clutches used to transmit power along the drivetrain of a vehicle.
  • Clutches are commonly used in vehicles to selectively transmit the rotation of an input member, such as a transmission shaft, to an output member, such as a gear.
  • a drum is attached to and rotates with the shaft.
  • a first set of driving plates operatively attached to the drum are interposed with a second set of driven plates operatively attached to the output member such as a gear.
  • a piston may be hydraulically actuated to engage and release the plates. Accordingly, when the plates are engaged, the friction force between the plates increases and transfers the rotation of the first set of plates to the second set.
  • the clutch is therefore used to control the gear output.
  • the clutch drum must adequately support the driving plates so that the plates do not slip when engaged. It is therefore typical for the drum to have radially extending teeth or splines formed about the perimeter of the drum which correspond to splines on the driving plates for adequately supporting the plates on the drum.
  • each successive rack tooth therefore increases the bend in the blank until the desired drum tooth shape and size are obtained.
  • excess material may be pushed along the periphery of the drum so that a wave of excess material gathers or "bunches" at a point on the blank which may ruin the drum.
  • Another known method is to machine the teeth into the drum. In this method, teeth are machined into the interior wall of a sufficiently thick cylindrical blank. The machining process, however, is not only relatively expensive, but also requires the use of a relatively thick blank to form the drum and results in wasted material.
  • Previously known clutches may have further problems resulting from the bending loads exerted on a backing plate of the clutch disposed behind both sets of plates. As the plates are compressed together, the backing plate provides a resisting force so that the plates engage one another. A retaining ring inserted in a groove in the drum limits movement of the backing plate in response to the clutch plates and piston. As the plates are forced against a typical backing plate, a bending moment is created which may create excessive forces on the drum which may ultimately damage the drum.
  • a general aim of the present invention is to provide an easy and inexpensive method for forming a clutch drum.
  • FIGURE 1 is a partially sectioned perspective view of a powershift clutch in accordance with the present invention.
  • FIG. 2 is a sectional side view of the clutch taken along line 2-2 of FIG. 1 showing the declutched position.
  • FIG. 3 is an enlarged sectional side view of the clutch taken along line 2-2 of
  • FIG. 1 showing the fully engaged position.
  • FIG. 4 is a top view of a drum made in accordance with the present invention and incorporated into the clutch of FIG. 1.
  • FIG. 5 is a sectional side view of the drum taken along line 5-5 of FIG. 4.
  • FIG. 6A is a perspective view of an initial drum blank which is ultimately formed into the drum of the present invention.
  • FIG. 6B is a perspective view of the drum blank of FIG. 6 A having a plurality of indentations pressed into the outer periphery of the flange.
  • FIG. 6C is a schematic illustration of the drum blank placed in a press having a die shaped to form teeth in the blank.
  • FIG. 6D is a perspective view of a completed drum.
  • FIG. 7 is an enlarged side view of a backing plate of the clutch of FIG. 1.
  • FIG. 8 is a schematic illustration showing the loading of a backing plate in accordance with the present invention.
  • FIG. 9 is a schematic illustration showing the loading of a conventional backing plate.
  • FIGS. 1-3 a clutch 10 mounted on a transmission shaft 12 for selectively operating left and right gears 14 is shown incorporating the clutch drum 16 in accordance with the invention.
  • FIGS. 1-3 illustrate a transmission shaft 12 having symmetrical left and right clutch drums and associated components. Reference will be made to the left drum clutch and associated components.
  • the drum 16 has an integral wall separated into small and large diameter walls 18, 20 by a flange 22.
  • the first end 24 of the drum forms an inwardly disposed base 26 and the second end 25 of the drum 16 defines a second end of a cavity 28.
  • the first end 24 has an opening 30 for slidably engaging the shaft 12 during assembly and is welded to the middle gear 14 generally at point 32 (FIG. 2).
  • the middle gear 14 is also welded to the shaft 12 at point 34 so that the drum 16 rotates in unison with the shaft 12.
  • the large diameter drum wall 20 defines a plurality of teeth or splines 36.
  • the splines 36 are adapted to receive corresponding splines 38 of a plurality of annular driving clutch plates 40 for forming a spline connection which permits the driving clutch plates 40 to rotate in unison with the transmission shaft 12.
  • the teeth 36 define a plurality of alternating troughs 42 and crests 44.
  • a circular slot 46 is formed near the second end 25 of the drum 16.
  • the slot 46 comprises a series of slot portions 47 formed in the troughs 42 and is sized to accommodate a portion of a retaining ring 48.
  • the gear 14 provides output from the transmission shaft 12 when the clutch is engaged. As best shown in FIGS. 2-3, the gear 14 has a central bore 15 supported on the transmission shaft 12 using bearings 50. Oil seals, retainer rings, bearings, and
  • the left and right gears 14 have a sleeve 52 concentric with the transmission shaft 12 which projects into the cavity 28 of the drum 16.
  • the outer diameter of the sleeve 52 has a plurality of splines 54.
  • a plurality of driven clutch plates 56 which extend outwardly from of the sleeve 52, have a plurality of splines 58 which engage the sleeve spline 54 to form a spline connection.
  • the driven clutch plates 56 are interposed between the driving clutch plates 40 to form a series of alternating driving and driven clutch plates 40, 56.
  • the interposed clutch plates 40, 56 may be selectively compressed and released to control the output of the gear 14.
  • a conventional oil actuated piston 60 may be used to compress and release the clutch plates 40, 56 as the piston 60 is positioned between a disengaged or declutched position shown in FIG. 2 and an engaged or fully clutched position shown in FIG. 3.
  • the piston 60 has a recessed wall 62 which, in conjunction with the walls 12a, 14a, 16a of transmission shaft 12, middle gear 14 and drum 16, respectively, form an annular cavity 64. Oil may be selectively supplied in a conventional manner to the cavity 64 through oil port 66 which is in fluid communication with an oil line 67 in the transmission shaft 12.
  • a backing plate 68 is attached to the drum 16 near the second end 25 to provide a surface against which the driving and driven clutch plates 40, 56 are compressed.
  • the backing plate 68 has a body portion 69 extending between the interior face of the drum wall 20 and the exterior face of the sleeve 52.
  • the body portion 69 has an elongated top face 71 which slidably engages a seal 73 in the sleeve 52 to prevent oil leakage therethrough.
  • the backing plate 68 has a body portion 69 extending between the interior face of the drum wall 20 and the exterior face of the sleeve 52.
  • the body portion 69 has an elongated top face 71 which slidably engages a seal 73 in the sleeve 52 to prevent oil leakage therethrough.
  • the backing plate 68 is attached to the drum 16 near the second end 25 to provide a surface against which the driving and driven clutch plates 40, 56 are compressed.
  • the backing plate 68 has a body portion 69 extending
  • the plate 68 (FIG. 7) has a plurality of teeth or splines 70 adapted for slidably engaging the drum spline 36 to form a spline connection.
  • the backing plate 68 has a generally flat engaging surface 72 disposed towards the clutch plates (FIG. 7).
  • the slot 46 in the drum 16 (best shown in FIGS. 4-5) is located on the rear or left side of the backing plate 68 (as shown in FIG. 2) and carries the retaining ring 48 which limits the leftward movement of the backing plate 68 and resists the forces exerted on the backing plate 68 by the clutch plates 40, 56 and the piston 60. Accordingly, the piston 60 compresses the clutch plates 40, 56 against the backing plate 68 to thereby engage the clutch 10.
  • a spring member 76 disposed about the circumference of the transmission shaft 12 overcomes the oil pressure and returns the piston 60 to the disengaged position, wherein the clutch plates 40, 56 are disengaged from each other.
  • the spring 76 is disposed inside the sleeve 52 between a retaining ring 78 disposed in a shaft slot 80 and a cut-off ring 82 adjacent to the piston 60.
  • the strength of the spring 76 is selected so that it overcomes a predetermined pressure level in the cavity 64 and thereby pushes the piston 60 to the disengaged position.
  • oil is directed through the driving and driven clutch plates 40, 56 to cool the heat generated from friction between the plates 40, 56.
  • a cooling oil inlet 84 in fluid communication with the lubrication line 86 inside the shaft 12, discharges inside the drum 16 near the spring 76. The oil flows radially from the shaft 12 towards the drum wall 20 in response to centrifugal forces.
  • the clutch plates 40, 56 preferably have arcuate grooves (not shown) on their surfaces which facilitate the flow of oil from the center to the periphery of the plates 40, 56 and the drum 16.
  • Axially aligned outlet holes 88 are located periodically throughout the drum 16 for allowing the oil to exit the drum 16.
  • the drum 16 has four lines of holes 88 spaced radially about the drum every 90 degrees.
  • the cut-off ring 82 controls the flow of cooling oil. As best shown in FIGS.
  • the cut-off ring 82 slidably engages the transmission shaft 12 and is located between the spring 76 and the piston 60.
  • the cut-off ring 82 is moved along the surface of the transmission shaft 12 (leftward in FIGS. 2-3) to expose the cooling oil inlet 84 as shown in FIG. 3 and allow oil to flow into the drum 16.
  • the spring 76 positions the cut-off ring 82 (rightward in FIGS. 2- 3) over the inlet as shown in FIG. 2 to restrict, without entirely stopping, oil flow.
  • maximum cooling oil flows through the clutch 40, 56 when the plates are engaged and most likely to generate heat.
  • the backing plate 68 is configured to reduce the bending moment Fj . resulting from loads applied from the clutch plates 40, 58 on the backing plate 68.
  • FIG. 9 which schematically illustrates the loading of a conventional backing plate 90 supported by a retaining ring 92
  • the clutch plates exert a load F 2 on the backing plate 90 which, in turn, exerts a load F 3 on the retaining ring 92. Since the load F 2 from the conventional backing plate 90, on the retaining ring 92 is greatest at a point furthest from an axis of bending 94, a relatively large bending moment is created which may damage the retaining ring 92 and the drum 16.
  • the backing plate 68 in accordance with the present invention has a rear face 96 disposed at a relief angle 98. The relief angle
  • the 98 is preferably inclined V «, to I 2 degrees from a radial plane of the drum 16.
  • the relief angle positions the load F 3 from the backing plate 68 on the retaining ring 48 closer to the axis of bending 94, minimizing the bending moment on the retaining ring
  • the drum 16 may also be formed in accordance with a novel and relatively inexpensive manufacturing method.
  • FIG. 6 A Conventional techniques may be used to obtain a drum blank 100 as shown in FIG. 6 A.
  • the drum blank 100 has smooth small and large diameter walls 102, 104 connected by a radially projecting flange 101.
  • the blank 100 forms the cavity 107 having the nearly closed first end 103 and open second end 105.
  • a plurality of angled indentations 108 are pressed into the periphery of the flange 101 using a die at points corresponding to the troughs 42 located between adjacent teeth 36, as illustrated in FIG. 6B.
  • the indentations 108 permit the flange 101 to remain substantially flat and planar after the teeth 36 are formed, thereby avoiding the creation of bulges in the flange 101 typically formed in conventional rack rolling methods, which cause stress concentrations and points of failure in the flange 101 and teeth 36.
  • the teeth 36 are formed in the large diameter wall 104 of the blank 100.
  • the blank 100 is indexed on a mandrel 110 resembling a spur gear, and at least one tooth 36 is formed in the blank 100 at each indexed position.
  • the preferred method for accomplishing this step is to use a punch press (illustrated schematically in FIG. 6C and indicated by reference numeral 112) carrying a die 114 shaped to form at least one tooth.
  • a punch press illustrated schematically in FIG. 6C and indicated by reference numeral 112
  • the blank 100 is positioned over the mandrel 110 and the die 114 is brought to the outside face of the large diameter wall 104 to form at least one tooth 36.
  • the die 114 is shaped so that it forms troughs 42 which extend radially inward from the large diameter wall 104 of the blank 100 to define each tooth 36.
  • the die 114 is sized so that it forms three teeth during each cycle, as best shown in FIG. 6C. It will, however, be appreciated that a die having more or less than three teeth may also be used.
  • the drum blank 100 is positioned over a mandrel and a cam die is forced against the outside of the blank 100.
  • the cam die is shaped to simultaneously form troughs 42 around the entire periphery of the blank 100.
  • the slot 46 for securing the retaining ring 48 is formed through each of the troughs 42.
  • the slot 46 is preferably formed using a punch press carrying a die which forms one slot portion 47 at a time in respective troughs 42 (FIG. 5).
  • the slot portions are formed so that they pass only partially into the thickness of the large diameter wall 104.
  • the slot portions 47 do not extend completely through the large diameter wall 104 which would create through holes which may otherwise increase stress concentrations in the wall 104.
  • the punch press may be used to shear the slot 46 entirely through the wall 104.
  • the shear cut may, however, result in the drum having undesirable stress concentrations in the areas of the through slots. It will therefore be appreciated that the formed slot portions 47 result in greater drum strength.
  • the punch press may again be used to punch a hole
  • the oil outlet holes 88 are formed in some of the teeth 36. According to the illustrated embodiment, the holes 88 are formed in four teeth which are radially spaced at 90 degree intervals. The number of holes in a drum, however, may be adapted to the oil flow of the particular application.
  • the present invention provides a new and improved powershift clutch and a method for making the same.
  • the clutch of the present invention advantageously incorporates a backing plate which minimizes the bending forces exerted on the retaining ring and the drum by creating an angled rear face to reduce the bending moment.
  • the present invention provides a relatively easy and inexpensive method for forming the drum of a clutch. The method may be carried out using a conventional punch press and therefore does not require expensive tooling.
  • the improved method does not create a wave of excess material created during many conventional methods. Instead, the present invention uses a mandrel and die to form a portion of the teeth and then indexes the drum to form more teeth.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un procédé permettant de réaliser un tambour d'embrayage (16) pourvu de dents disposées radialement, au moyen d'une presse à découper. Un ébauche de tambour est indexée sur un mandrin (110) et une matrice (112) montée sur la presse à découper forme des dents à chaque emplacement correspondant à l'indexage. Ce procédé évite la création d'une vague de matériau excédentaire à laquelle on doit s'attendre lors de la mise en oeuvre des procédés connus. L'invention concerne également un plateau d'appui (68) destiné à être utilisé dans un embrayage couplable sous charge (10), qui présente un angle de dépouille servant à réduire le moment de flexion créé lorsque ledit plateau d'appui est sous charge, lequel pourrait endommager le tambour.
PCT/US1997/011266 1997-06-27 1997-06-27 Embrayage couplable sous charge et son procede de realisation Ceased WO1999000199A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/US1997/011266 WO1999000199A1 (fr) 1997-06-27 1997-06-27 Embrayage couplable sous charge et son procede de realisation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1997/011266 WO1999000199A1 (fr) 1997-06-27 1997-06-27 Embrayage couplable sous charge et son procede de realisation

Publications (1)

Publication Number Publication Date
WO1999000199A1 true WO1999000199A1 (fr) 1999-01-07

Family

ID=22261171

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1997/011266 Ceased WO1999000199A1 (fr) 1997-06-27 1997-06-27 Embrayage couplable sous charge et son procede de realisation

Country Status (1)

Country Link
WO (1) WO1999000199A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003027525A3 (fr) * 2001-09-21 2003-09-04 Zf Sachs Ag Systeme d'embrayage multiple pourvu d'ensembles d'embrayage multidisque juxtaposes dans le sens axial
JP2009241106A (ja) * 2008-03-31 2009-10-22 Mazda Motor Corp 円筒状クラッチ部品の成形方法及び成形装置
WO2022117144A1 (fr) * 2020-12-03 2022-06-09 Schaeffler Technologies AG & Co. KG Dispositif à friction doté d'un élément ressort de rappel, et dispositif de transmission
DE102021108593A1 (de) 2021-04-07 2022-10-13 Schaeffler Technologies AG & Co. KG Hydraulikanordnung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2829041A1 (de) * 1978-07-01 1980-01-10 Volkswagenwerk Ag Verfahren und vorrichtung zur herstellung eines innen- und aussenverzahnten topffoermigen blechteils
JPS5758941A (en) * 1980-09-26 1982-04-09 Marujiyun Seiki Kogyo Kk Manufacture of transmission parts such as toothed pulley, toothed wheel

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2829041A1 (de) * 1978-07-01 1980-01-10 Volkswagenwerk Ag Verfahren und vorrichtung zur herstellung eines innen- und aussenverzahnten topffoermigen blechteils
JPS5758941A (en) * 1980-09-26 1982-04-09 Marujiyun Seiki Kogyo Kk Manufacture of transmission parts such as toothed pulley, toothed wheel

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003027525A3 (fr) * 2001-09-21 2003-09-04 Zf Sachs Ag Systeme d'embrayage multiple pourvu d'ensembles d'embrayage multidisque juxtaposes dans le sens axial
JP2009241106A (ja) * 2008-03-31 2009-10-22 Mazda Motor Corp 円筒状クラッチ部品の成形方法及び成形装置
WO2022117144A1 (fr) * 2020-12-03 2022-06-09 Schaeffler Technologies AG & Co. KG Dispositif à friction doté d'un élément ressort de rappel, et dispositif de transmission
CN116438386A (zh) * 2020-12-03 2023-07-14 舍弗勒技术股份两合公司 具有复位弹簧元件的摩擦设备和变速器设备
DE102021108593A1 (de) 2021-04-07 2022-10-13 Schaeffler Technologies AG & Co. KG Hydraulikanordnung

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