US3261166A - Converter - Google Patents

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Publication number
US3261166A
US3261166A US442650A US44265065A US3261166A US 3261166 A US3261166 A US 3261166A US 442650 A US442650 A US 442650A US 44265065 A US44265065 A US 44265065A US 3261166 A US3261166 A US 3261166A
Authority
US
United States
Prior art keywords
working chamber
converter
pump
wheel
sump
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
US442650A
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English (en)
Inventor
Volker Heinz
Weis Alfred
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.)
ELMEG Elektro Mechanik GmbH
Original Assignee
ELMEG Elektro Mechanik GmbH
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 ELMEG Elektro Mechanik GmbH filed Critical ELMEG Elektro Mechanik GmbH
Application granted granted Critical
Publication of US3261166A publication Critical patent/US3261166A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F16H61/14—Control of torque converter lock-up clutches

Definitions

  • the present invention relates generally to the torque converter art, and, more particularly, to a Foettinger converter which is extraordinarily short and compact.
  • the use of positively operating by-pass couplings within the inner diameter of the working chamber although conventional are disadvantageous because the parts which are to be coupled must be synchronized before the coupling takes place.
  • the positively connected or force-locked operating by-pass couplings are positioned laterally of the working chamber so that they tend to increase the total length of the converter.
  • Another object of the invention is to provide a converter of the character described wherein the transmission ratio and the power consumption will not be worse or smaller than in conventional converters which are provided with the same outer diameter but have much larger outer dimensions otherwise and larger ilow passage cross sections.
  • Still another object of the invention is to provide a converter wherein the axial passages of the converter which provide for hydraulic flow are shortened in order to reduce the losses caused by friction.
  • Yet another object of the invent-ion is to provide a device of the character described which eliminates the disadvantages of prior art devices as set forth above.
  • a Foettinger converter having an annular working chamber which is the chamber where the transfer of power takes place between the pump blades and the turbine blades.
  • the maximum width or axial length of the working chamber is percent of the outer diameter of this chamber and the minimum inner diameter is 35 percent of the outer diameter. Utilizing these proportions provides that the blades are positioned on a relatively large radius and are therefore particularly effective.
  • the sump pump in the present invention is disposed within the hub casing and a driving connection of the pump wheel and turbine wheel is provided in the hub of the casing by means, for example, of a direct drive friction clutch.
  • FIGURE 1 is a partial sectional view through one em bodiment of the present invention.
  • FIGURE 2 is a partial sectional view through another embodiment of the invention.
  • FIGURE 1 an outer casing 13 is provided and a drive shaft 1 is disposed at the left side while a driven shaft 4 is provided on the right side thereof.
  • a fixed converter housing 5 which is actually the housing for the working chamber 5'.
  • a converter pump wheel 2 is connected to a hub 10 which is mounted to drive shaft 1.
  • the hydraulic fluid which is accelerated by pump 2 by means of its blade 8, streams in the converter Working chamber 5' and drives the turbine 3 of the converter by causing the hydraulic fluid to move against the turbine blades 9.
  • turbine wheel 3 is mounted on the drive shaft 4.
  • the pump blades 8 are provided for streaming a liquid against the turbine blades 9. Also provided is a reaction member in the form of guiding blades 6 which are connected to the fixed housing 5 to provide smooth conditions of flow from the initial direction at the inlet of the pump 2.
  • the converter working chamber which is annular is so formed that its width or axial length B is less than or equal to 20 percent of the outer diameter Da, and the inner diameter -Di is greater than or equal to 35 percent of the outer diameter Da.
  • FIGURE 1 From the embodiment of the present invention as set forth in FIGURE 1 it can be seen that in the converter of the present invention all of the blades, that is the pump blades 8, the turbine blades 9, and the guide or control blades 6, are disposed on a very large radius so that they have a high circumferential speed even at low drive rpm. of the pump wheel 2 and they thereby become effective as a power transmission. Therefore the otherwise conventional high gear drive before the drive shaft 1 can be eliminated.
  • the construction of the present invention permits the arrangement of the sump and pressure maintaining pump 11 on the drive shaft 1 at or in the pump hub 10.
  • a special drive for the pump is not necessary so that power transmission elements such as chain and gear drives which are susceptible to trouble and which normally are necessary and which would enlarge the dimensions of the converter in an undesirable manner, can be omitted.
  • FIGURE 1 the converter of the present invention is shown which has a by-pass coupling 12 in addition to the sump and pressure maintaining pump 11 installed in the pump hub 10.
  • this coupling 12 is positioned between the pump hub 10 and the drive shaft 4.
  • FIGURE 1 illustrates a converter having a sump and pressure maintaining pump for the working chamber as well as means providing a driving connection of the pump wheel and turbine wheel in the hub casing.
  • the sump and pressure maintaining pump is positioned within the inner diameter of the annular working chamber.
  • the means for providing a driving connection of the pump wheel and turbine wheel 3 within the inner diameter of the annular working chamber and such could take the form, for example. of a positive operating by-pass coupling as shown in FIGURE 2.
  • FIGURE 2 is an embodiment of the invention in which the means for drivingly connecting the pump wheel and the turbine wheel is disposed Within the inner diameterof the annular working chamber.
  • this means is a positively operating multiple disc clutch operated by oil pressure and made effective by an automatic control device (not shown) when the secondary moment is equal to the primary moment.
  • Elements in FIGURE 2 which are similar to those of FIG- URE 1 are identified with similar reference numerals, but preceded by 2.
  • the converter of the present invention it is possible to arrange means for a driving connection of the pump wheel and turbine wheel in the hub casing so that the length of the converter is not increased by this installation. It is also possible to place the sump and pressure maintaining means in the hub casing of the converter. This, too, does not contribute to an increase in the total length of the converter.
  • the converter constructed in accordance with the present invention with all of the auxiliary assemblies consequently forms a compact, extremely short arrangement whereas in the conventional converter arrangements the auxiliary assemblies are annexed to the actual converter and unnecessarily enlarge its dimensions.
  • the sump pump in the conventional arrangements is particularly very susceptible to trouble because it is driven via chain or gear drives so that the sump pump necessarily has to be positioned on the outside of the converter in order to provide easy accessibility.
  • this problem is solved in a simple manner by positioning the sump pump in the hub of the converter to rotate with it. Intermediate gearing and drives which are susceptible to trouble are thus eliminated.
  • a torque converter having sump and pressure maintaining means for the annular working chamber thereof and means for firmly connecting the pump wheel and the turbine wheel, the improvement wherein the width of the working chamber is not more than 20 percent of the outer diameter of the working chamber and the inner diameter of the working chamber is not less than 35 percent of the outer diameter.
  • a torque converter comprising, in combination:
  • (c) means defining an annular working chamber in which a hydraulic fluid impelled by the pump wheel drives the turbine wheel, the Width of the working chamber being not more than 20 percent of the outer diameter of the working chamber and the inner diameter of the working chamber being not less than 35 percent of the outer diameter;
  • a torque converter comprising, in combination:
  • (c) means defining an annular working chamber in which a hydraulic fiuid impelled by the pump wheel drives the turbine Wheel, the width of the working chamber being not more than 20 percent of the outer diameter of the Working chamber and the inner diameter of the working chamber being not less than 35 percent of the outer diameter;

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Fluid Gearings (AREA)
US442650A 1964-03-25 1965-03-25 Converter Expired - Lifetime US3261166A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DEE26700A DE1265520B (de) 1964-03-25 1964-03-25 Hydrodynamischer Drehmomentwandler

Publications (1)

Publication Number Publication Date
US3261166A true US3261166A (en) 1966-07-19

Family

ID=7072301

Family Applications (1)

Application Number Title Priority Date Filing Date
US442650A Expired - Lifetime US3261166A (en) 1964-03-25 1965-03-25 Converter

Country Status (5)

Country Link
US (1) US3261166A (de)
AT (1) AT250119B (de)
DE (1) DE1265520B (de)
GB (1) GB1055113A (de)
SE (1) SE308644B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3320747A (en) * 1965-09-10 1967-05-23 Borg Warner Hydrokinetic drive

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5430359A (en) * 1977-08-12 1979-03-06 Komatsu Ltd Fluid change-gear
AU8568882A (en) * 1981-07-20 1983-01-27 Borg-Warner Corporation Torque converter
DE3134857C2 (de) * 1981-09-03 1985-11-21 Bayerisches Leichtmetallwerk Graf Blücher von Wahlstatt GmbH & Co KG, 8000 München Verfahren zum Herstellen von Kupplungsteilen

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1298990A (en) * 1917-04-12 1919-04-01 William H Mason Gearless power transmission.
US1921014A (en) * 1929-03-02 1933-08-08 Carl W Weiss Transmission
DE525027C (de) * 1929-10-18 1931-05-20 Johann Nikolaus Kiep Dipl Ing Einrichtung zum Fuellen der Kreislaeufe von Fluessigkeitsgetrieben nach Art der Foettinger-Getriebe
US2212278A (en) * 1938-01-15 1940-08-20 Sinclair Harold Variable-speed power-transmission mechanism
US2462652A (en) * 1943-08-25 1949-02-22 Jarvis C Marble Rotary converter-coupling hydraulic power transmission
US2578876A (en) * 1946-02-06 1951-12-18 Otto A Banner Hydraulic torque converter having radial and axial stages

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3320747A (en) * 1965-09-10 1967-05-23 Borg Warner Hydrokinetic drive

Also Published As

Publication number Publication date
DE1265520B (de) 1968-04-04
SE308644B (de) 1969-02-17
AT250119B (de) 1966-10-25
GB1055113A (en) 1967-01-18

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