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
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D41/00—Freewheels or freewheel clutches
  • F16D41/22—Freewheels or freewheel clutches with clutching ring or disc axially shifted as a result of lost motion between actuating members
• • 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
  • F16H41/04—Combined pump-turbine units

Definitions

• This invention relates to hydrodynamic torque converter-couplings of the kind comprising an impeller member, a turbine member and a reaction member which are mounted for independent rotation about a common axis, together define a toroidal working circuit for a working liquid and each have guide vanes for interacting with the liquid within the working circuit in such a manner that when the turbine member is stationary or rotating at a speed which is low compared with, that of the impeller member, the torque applied to the turbine member by the liquid is greater than the input torque acting on the impeller, the algebraic difference in the two said torques being compensated by a backward reaction torque applied by the liquid to the reaction member which is temporarily held stationary.
• the relative axial movement between the abutment surfaces into engagement may be effected by a helical constraint of limixed length between a nember carrying one set of the abutment surfaces and the reaction member, relative movement along the constraint being at least initiated by a drag torque exerted by drag means.
• the abutment surfaces may conveniently be formed by tooth surfaces of a toothed clutch.
• the opposite surfaces of the clutch teeth are inclined to the axis to assist axial separation of the toothed clutch when the output speed rises to the coupling range.
• a torque converter-coupling in which the guide vanes of the reaction member are inclined to the axis, wherein the reaction member is mounted for limited movement in the axial direction, and axial movement of the reaction member in response to the axial component of force exerted by the liquid on the reaction member guide vanes is arranged to engage and disengage a holding clutch for the reaction member.
• the torque converter-coupling embodies both aspects of the invention.
• a lock-up clutch may be provided for selectively locking the input member to the output member.
• Figure 3 is a fragmentary view oh an enlarged scale in the direction of the line III-III of Figure 2;
• Figure 4 is a view in the direction of the arrow IV of Figure 3;
• Figure 5 is an axial sectional view of a hub portion of a modified torque converter-coupling in accordance with the invention
• Figure 6 is a plan view of the friction band of
• FIG 7 is a cross-sectional view through the friction band and co-operating sleeve of Figure 5.
• the torque converter-coupling shown in Figure 1 is of generally conventional construction in that it includes an impeller member 1, a turbine member 2 and a reaction member 3 which together define a toroidal working circuit 4.
• Each of the three elements 1, 2, 3 is formed with a set of guide vanes 1a, 2a, 3a, each set of guide vanes terminating in an annular core portion lb, 2b, 3b, which together form a toroidal core for the working circuit 4.
• the guide vanes- are angled and/or curved to obtain the required performance of the converter-coupling and in particular, the guide vanes 3a of the reaction member 3, whether curved or not, are inclined to the axis of the coupling.
• the turbine member 2 is bolted to a flange 11 which is connectec by splines 13 to an output shaft 12.
• the inner (left-hand) end 14 of the shaft 12 is journalled by means of a ball-bearing 15 in the input member 8 and a radial-roller thrust bearing IS is mounted between the flange 11 and the input member 8.
• the other end of the shaft 12 is journailed or otherwise supported in a stationary casing 17 having a sleeve portion 18 surrounding the shaft 12 with clearance.
• the radially outer surface of the hub 25 is splined to engage in corresponding splines 27 in a central bore in the reaction member 3.
• a pair of spring rings 28 engaged in the bore in the reaction member 3 engage the end surfaces of the hub 25 to locate the latter relative to the reaction member.
• the range of axial movement of the hub 25 and thus of the reaction member assembly, is limited by end rings 29 and 30 welded or otherwise secured to ⁇ he sleeve member 19 and forming each a race of the respective bearing 2 4, 23.
• the end ring 30 and the adjacent end of the hub 25 are formed with complementary sets of shallow clutch teeth 31, 32.
• the clutch teeth each have a substantially radial and axial abutment face 33 on one flank, the other flank 34 of each tooth being relatively long and gently sloping.
• the tips 35 of the teeth are narrow and flat and correspondingly flat and narrow lands 36 are formed at the roots of the flanks 33, 34.
• the direction of liquid flow through the reaction member blade 3a is at: an angle to these blades such as to exert an axial force on the reaction member assembly 3 which moves the latter (to the right in Figures 1 and 2) to being the two sets of clutch teeth 31 and 32 into full engagement.
• the reaction member 3 will then be prevented from rotating as a result of mutual engagement of the abutment surfaces 33 on the two sets of clutch teeth.
• the friction material 43 and the resilient force with which it is applied to the outer surface of the sleeve member 19 can be chosen to provide the required drag torque opposing rotation of the reaction member 3 and thus to determine the axial force exerted on the reaction member 3 during transitions between the locked and unlocked states and vice versa of the reaction member.
• centrifugal force will cause the band 41 to expand against its internal.resilience until the drag torque is eliminated, or reduced to an acceptable value.
• the reaction member 3 is splined onto a sleeve 51 (with straight splines 52).
• the handing of the splines 53 and teeth 54,55 is furthermore chosen such that the transfer of this drag torque through the teeth 54 and 55 and the helical splines 53 to the reaction member 3 results in an axial force on the hub 25' to the right in Figure 5 to engage the clutch teeth 32 with the teeth 31.
• connection between the band 57 and the hub 25' may by made by fixing a peg, such as the peg 45 of Figure 2, to the band 57 near the appropriate end of the latter, the hub 25' then being formed with a slot to accommodate this peg, the slot being of sufficient length axially of the hub to permit the necessary axial movement of the hub.
• a peg such as the peg 45 of Figure 2

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Mechanical Operated Clutches (AREA)

Priority Applications (1)

Applications Claiming Priority (2)

Publications (1)

Family

ID=10521904

Family Applications (1)

Country Status (4)

Cited By (6)

Citations (3)

• 1982
  • 1982-05-18 EP EP19820901634 patent/EP0079365A1/de not_active Withdrawn
  • 1982-05-18 JP JP50162882A patent/JPS58501004A/ja active Pending
  • 1982-05-18 WO PCT/SE1982/000178 patent/WO1982004109A1/en not_active Application Discontinuation
  • 1982-05-18 BR BR8207699A patent/BR8207699A/pt unknown

Patent Citations (3)

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