US3824038A - Cooling device for hydraulic torque converters - Google Patents

Cooling device for hydraulic torque converters Download PDF

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Publication number
US3824038A
US3824038A US00393815A US39381573A US3824038A US 3824038 A US3824038 A US 3824038A US 00393815 A US00393815 A US 00393815A US 39381573 A US39381573 A US 39381573A US 3824038 A US3824038 A US 3824038A
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US
United States
Prior art keywords
cooling device
blades
shell
annular members
impeller
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.)
Expired - Lifetime
Application number
US00393815A
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English (en)
Inventor
M Tokunaga
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.)
Exedy Corp
Original Assignee
Daikin Manufacturing Co Ltd
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 Daikin Manufacturing Co Ltd filed Critical Daikin Manufacturing Co Ltd
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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
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H41/30—Details relating to venting, lubrication, cooling, circulation of the cooling medium

Definitions

  • This invention relates to a novel cooling device for hydraulic torque converters.
  • torque converters and particularly those forming part of the driving assembly of automotive vehicles, are inherently subject to undesirable heating during operation.
  • the working fluid is compressed, forced to flow rapidly and transmit considerable amounts of energy during operation. It therefore follows that the internal friction of the fluid causes a sharp temperature rise which results in deterioration of the fluid performance.
  • Prior efforts to dissipate this heat has not been satisfactory.
  • these structures have been so expensive to assemble as to increase excessively the cost of torque converters.
  • a prior type cooling device comprises a multiplicity of separate thin fins or other blade like members, each fin being secured individually on and projecting from the exterior surface of the impeller shell.
  • a principal object of the invention is to provide an improved cooling device having many radial ribbed blades connected by one or more annular ribs to form a unitary structure which is secured on the exterior surface of the impeller shell to not only increase the heat radiation capacity but to produce a composite structure of greater rigidity and durability.
  • Another object of the invention isto provide a cooling structure of greatly increased demension stability so that the blades will not loosen, the distance between the blades will not change with use time and the profile of a blade will not change, because each blade is strengthened and reenforced by the radial rib and preferably is integral therewith, preferably being stamped in one piece from sheet metal.
  • a further object of the invention is to provide a cooling device which simplifies assembly since a position setting jig is not necessary therein, permitting a lower cost of manufacture.
  • FIG. 1 is a sectional view of an upper half of a torque converter according to the present invention
  • FIG. 2 is a perspective view taken from inside of the fin embodying principles of the invention
  • Torque converter 10 comprises a drive impeller wheel (i.e., an impeller) 11; a driven impeller wheel (i.e., a turbine) 12; and a stator 13; the drive impeller wheel 11 being adapted to transmit energy to an inner working fluid, and in turn turbine 12 receives energy from such fluid.
  • Stator 13 is fixed below a predetermined output-input speed ratio, to change the direction of the fluid to convert the energy thereof.
  • Impeller 11 is connected to an engine flywheel 14 to which the outer periphery of drive plate 15 is secured by bolts 16 and the inner part of the drive plate is secured by bolts 17 to a hub 18 and support ring 19.
  • An axle 20 of the hub 18 is journaled in flywheel 14 by a bearing 21.
  • a drive plate 22 is secured to support ring 19 as by weld 23 and a support ring 25 is also secured thereto as by weld 24.
  • Around support ring 25 is a support ring 27 which is fastened to support ring 25 by bolts 26 and a liquid tight seal is provided therebetween by seal ring 28.
  • Turbine 12 is fixed on a spline hub 20 by means of rivets 29, and, in turn, this hub 30 engages with a spline 32 on a driven shaft (i.e. a turbine shaft) 31.
  • Turbine shaft 31 is journaled on a bearing 33 mounted inside hub 18 and support ring 19.
  • a ring 34 prevents the shaft 31 from slipping off axially.
  • Stator preferably is cast in one piece, and is journaled on a fixed sleeve 35 through a one-way clutch 36, which includes an outer race 37 which engages with stator 13 through spline 38.
  • stator is fixed on a stationary sleeve 35, while at a velocity above said velocity ratio, the stator is free to rotate in the same direction as that of driven impeller wheel or turbine 12, to make the converter act as a fluid coupling.
  • the shell 39 of impeller 11 is stamped from a heavy steel plate, and has a semi-toroidal inner surface.
  • annular part 40 of shell 39 is secured to support ring 27 as by welded joint 40' and a part 41 of shell 39 is secured to'an impeller hub 42 as by welded joint 41'.
  • a stamped cooling fin 43 is secured to the exterior surface of shell 39 as by welding.
  • the cooling fin 43 radiates the heat effectively in the present invention.
  • the cooling fin is a unitary structure comprising a multiplicity of blades 44, each of which blades has a radial rib 45 connected at its inner end with an inner annular member 46 and at its outer end with an outer annular member 47 to form a strong and structurally rigid member.
  • Each of ribs 45, 46, 47 has a configuration complementary to that of the exterior surface of shell to provide a snug fit therebetween as shown in FIG. 1.
  • marks X indicate places where spot welding is applied.
  • each radial rib 45 has one mark X
  • inner and outer annular members 46, 47 have four and eight marks respectively.
  • Spot welded portions are shown as at 48 in FIG. 1.
  • each blade 44 stands at the edge of radial rib 45 forming therewith an L section and has an even height from the exterior surface of radial rib 45, see FIGS. 3 and 4.
  • the radial rib 45 reenforces and materially increases the strength of ribbed blade 44, Le, the radial rib 45 holds the blade 44 rigidly along its entire root portion and acts to connect the blade 44 to shell 39.
  • Inner and outer annular members connect and keep ribbed blades in fixed predetermined position. Accordingly, the blades will not loosen as use time passes thereby preventing noise and separation of the blades.
  • the fin 43 shown inFlG. 2 may be manufactured by the process comprising; press forming an annular depression on a steel plate having a thickness of 0.8 to 1.0 mm, which depression has a configuration complementary to that of the exterior surface of shell 39, cutting three rims 44a, 44b, 44c of the blade 44 and simultaneously bending the blade, and cutting off the inner and outer parts leaving inner and outer annular members 46, 47 behind.
  • fin 43 When assembling fin 43 and shell 39, fin 43 is simply placed on shell 39, and the position of fin 43 is automatically set. Then the two parts are spot welded as at points X indicated in FIG. 2 without the necessity for position setting jigs.
  • fin 43 dissipates the heat of impeller 11 through blades 44 which conduct the heat away from shell 39 and transmit it to the air flow generated by blades 44.
  • Spiral blades (not shown) may be employed instead of radially straight blades 44.
  • the cooling device forms a high efficiency, open type centrifugal blower and smooth air flow may be obtained.
  • one of the inner or outer annular members 46, 47 may be eliminated.
  • a cooling device for a hydraulic torque converter including an impeller shell comprising a plurality of ribbed blades and at least one of inner and outer annular members, each of said blades having a radial rib forming apart thereof, said ribs being connected to said annular members to form a unitary structure, each of said radial ribs and said annular members having a configuration complementary to that of the exterior surface'of said impeller shell, means for securing said unitary structure to the exterior surface of said impeller shell.
  • a cooling device in which said ribbed blades and said annular members are formed in a one stamping.
  • a cooling device in which said ribbed blades are connected to both said inner and outer annular members.
  • a cooling device in which each of said ribbed blades is spiral.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • General Details Of Gearings (AREA)
US00393815A 1972-09-11 1973-09-04 Cooling device for hydraulic torque converters Expired - Lifetime US3824038A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP47091612A JPS4946055A (OSRAM) 1972-09-11 1972-09-11

Publications (1)

Publication Number Publication Date
US3824038A true US3824038A (en) 1974-07-16

Family

ID=14031379

Family Applications (1)

Application Number Title Priority Date Filing Date
US00393815A Expired - Lifetime US3824038A (en) 1972-09-11 1973-09-04 Cooling device for hydraulic torque converters

Country Status (6)

Country Link
US (1) US3824038A (OSRAM)
JP (1) JPS4946055A (OSRAM)
CA (1) CA976842A (OSRAM)
FR (1) FR2199080B1 (OSRAM)
GB (1) GB1432597A (OSRAM)
IT (1) IT994217B (OSRAM)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5005356A (en) * 1987-05-27 1991-04-09 Saunders Walter S Torque converter utilizing streamwise vorticity
WO1992017710A1 (en) * 1987-05-27 1992-10-15 Walter Selden Saunders Torque converters utilizing streamwise vorticity
US5616002A (en) * 1993-10-02 1997-04-01 Zf Friedrichshafen Ag Device for the transmission of moment from a drive unit to a transmission using a hydrodynamic converter
US20160131236A1 (en) * 2014-11-06 2016-05-12 Schaeffler Technologies Gmbh & Co. Kg Necked impeller shell for torque converter

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2216747A (en) * 1935-09-06 1940-10-08 Gustav A Klimek Blade construction for fluid power transmitter
US2428728A (en) * 1944-05-18 1947-10-07 United Specialties Co Turbine wheel
US2556676A (en) * 1944-06-09 1951-06-12 Gen Motors Corp Rotor blade construction
US2692560A (en) * 1950-12-15 1954-10-26 Borg Warner Cooling device for hydraulic torque converters
US2745354A (en) * 1950-04-22 1956-05-15 Borg Warner Hydrodynamic coupling
US3101672A (en) * 1960-04-27 1963-08-27 Renault Methods of manufacturing hydrodynamic torque transmitters

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1627506A1 (de) * 1967-04-07 1971-01-07 Fichtel & Sachs Ag Verfahren zur Herstellung eines Schaufelrades

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2216747A (en) * 1935-09-06 1940-10-08 Gustav A Klimek Blade construction for fluid power transmitter
US2428728A (en) * 1944-05-18 1947-10-07 United Specialties Co Turbine wheel
US2556676A (en) * 1944-06-09 1951-06-12 Gen Motors Corp Rotor blade construction
US2745354A (en) * 1950-04-22 1956-05-15 Borg Warner Hydrodynamic coupling
US2692560A (en) * 1950-12-15 1954-10-26 Borg Warner Cooling device for hydraulic torque converters
US3101672A (en) * 1960-04-27 1963-08-27 Renault Methods of manufacturing hydrodynamic torque transmitters

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5005356A (en) * 1987-05-27 1991-04-09 Saunders Walter S Torque converter utilizing streamwise vorticity
WO1992017710A1 (en) * 1987-05-27 1992-10-15 Walter Selden Saunders Torque converters utilizing streamwise vorticity
US5616002A (en) * 1993-10-02 1997-04-01 Zf Friedrichshafen Ag Device for the transmission of moment from a drive unit to a transmission using a hydrodynamic converter
US20160131236A1 (en) * 2014-11-06 2016-05-12 Schaeffler Technologies Gmbh & Co. Kg Necked impeller shell for torque converter
US10024409B2 (en) * 2014-11-06 2018-07-17 Schaeffler Technologies AG & Co. KG Necked impeller shell for torque converter

Also Published As

Publication number Publication date
FR2199080A1 (OSRAM) 1974-04-05
DE2345770B2 (de) 1975-12-11
IT994217B (it) 1975-10-20
JPS4946055A (OSRAM) 1974-05-02
GB1432597A (en) 1976-04-22
CA976842A (en) 1975-10-28
DE2345770A1 (de) 1974-04-04
FR2199080B1 (OSRAM) 1974-11-08

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