Patent GB-1038547-A (GB)
Title: Hydrokinetic torque converter mechanism with dual performance range
IPC: F16H41/26
Filed: 1963-10-17
Abstract: 1,038,547. Hydraulic torque converters; friction clutches; change-speed gears. FORD MOTOR CO. Ltd. Oct. 17, 1963 [Nov. 5, 1962], No. 40989/63. Headings F2C and F2D. An hydrodynamic torque converter for use with an automatically controlled change-speed gear in a motor car comprises at least a main impeller, a reactor and a turbine, and also an axially movable auxiliary impeller which can be friction clutched to the main impeller. An engine-powered shaft 10 is fast with the main impeller 34 of a torque converter having a turbine 38 connected to a sun gear 54, and a reactor 58 mounted by way of the usual one-way detent 70. Between the impeller 34 and the turbine 38 an axiliary impeller 90 is journalled. A friction clutch disc 108 on the back of the auxiliary impeller can engage with the casing 18 of the converter when the auxiliary impeller moves axially. Such axial movement is permitted either by play in the connection between the auxiliary impeller 90 and its shroud ring, or by flexing of fingers 88 carrying the auxiliary impeller. When the main impeller 34 begins to rotate, liquid flows through the working space of the converter and to both sides of a shell 98 carrying the auxiliary impeller. If the space between the shell 98 and the torque converter casing 18 is vented to sump through passages 112, 128, 124, the pressure of liquid in the converter working space engages the clutch disc 108 with the converter casing 18, so that the auxiliary and main impellers 90, 34 are clutched together. If a valve (not shown) in the vent passage 124 is shut, liquid pressure builds up in the space between the shell 98 and the casing 18 to disengage the clutch disc 108. The auxiliary impeller then rotates freely. Engagement and disengagement of the auxiliary impeller 90 from the main impeller 34 varies the characteristics of the converter. With the auxiliary impeller 90 running free, the torque ratio of the converter is increased at low running speeds. With the auxiliary impeller 90 clutched to the main impeller 34, better efficiency is obtained at higher speeds in the coupling range. The auxiliary impeller 90 drives through a sleeve shaft 80 to a multi-disc clutch 162 engaged against the bias of a spring 170 when liquid under pressure is admitted to a space 166 enclosing a servo piston 168, the clutch transmitting drive to a sun gear 56. Change-speed gear.-The turbine-driven sun gear 54 meshes planet pinions 130 also meshing planet pinions 132 meshed by the auxiliaryimpeller-driven sun gear 56. The intermeshing planet pinions 130, 132 are mounted in a carrier fast with an output shaft 146. The planet pinions 132 also mesh a reaction ring gear 140 which can be stationed by a band brake 144. On disengagement of the multi-disc clutch 162, the sun gear 56 can be stationed by a band brake 160. Low speed is established by engaging the brake 160 to station the sun gear 56, the turbine-driven sun gear 54 transmitting torque to the output shaft 146. High speed in the coupling range with torque splitting is established by instead engaging the auxiliary impeller clutch 108 to cause the auxiliary and main impellers 34, 92 to rotate together, and also engaging the multi-disc clutch 162, so that the sun gear 56 is mechanically clutched to the engine - powered shaft 10. Simultaneously torque is transmitted through the converter turbine 38 to the sun gear 54. Reverse is established by disengaging both clutches 108, 162 and instead engaging the band brake 144 to station the ring gear 140.