CS196845B1 - MULTIPLE AUTOMATIC PLANET GEARBOX - Google Patents

Abstract

The invention aa relates to a multi-stage automatic planetary gearbox with centrifugal radiating clutches equipped with a force-spinning mechanism and with auxiliary centrifugal weights guided by a reaction member of the transmission, which is particularly suitable for changing higher gear ratios of motor vehicle gearboxes.

Description

DESCRIPTION OF THE INVENTION R E P U BLIC 19 'TO COPYRIGHT CERTIFICATE (61)

(23) Show Priority (22) Registered 21.11.77 (21) (PV 7634-77) 196845 (11) (B1) (51) Int. Cl. 'B 62 M 11 / 14B 60 K 17/06

OFFICE OFFICE

AND DISCOVERIES (40) Published 31.07.79 (45) Published 31 * 03.82 (75)

The inventor

Bednar Jiri ing., Povazska Bystrica

MULTIPLE AUTOMATIC PLANET GEARBOX

The present invention relates to a multi-stage automatic planetary gearbox with centering shift clutches equipped with a power return mechanism with auxiliary centrifugal weights guided by a transmission reaction member, particularly suitable for shifting higher gear ratios of motor vehicle transmissions.

A known embodiment of multi-stage automatic planetary gear units with centrifugal shift clutches with a force feedback mechanism and auxiliary centrifugal weights guided by the transmission reaction member does not allow the desired effect of the auxiliary centrifugal weights to reduce the speed shift range in the partial retraction area, even when fully retracted The engine does not suffice a slight increase in the driving force of the engine when the engine speed is reduced to compensate for the increase in the transferable transmission due to the centrifugal force of the auxiliary centrifugal weights of the gearbox. This, in theory, is the immediate drop in engine speed at the final phase of the shifting and impact in the driving group when the engine is fully retracted, unless the effect of the auxiliary centreline weights to reduce shifting in the most needed partial engine load is limited to an insignificant minimum.

These drawbacks are eliminated by the multi-stage automatic planetary gearbox of the present invention. The essence of this is that the auxiliary centrifugal loads are in the space limited by the contact surface and the bearing surface of the auxiliary lamella, by the bottom recessed and by the spring reaction of the reaction member of the transmission, the spring-loaded reaction abutting against the protrusion of the reaction member of the transmission. An advantage of the step-by-step automatic planetary gearbox of the invention is that it allows the desired gear shift to be utilized in the area of partial retraction of the engine without reversing the smoothness of the shifting when the engine is fully loaded.

FIG. 1 is a cross-sectional view of a multi-stage automatic planetary gearbox of the present invention and a multi-plate centrifugal shift clutch provided with a force-retaining mechanism. FIG. 2 illustrates an embodiment of a multi-stage automatic planetary gearbox according to the invention, for example, a shift from 3 to 4 gear. The passages P and revolutions and, depending on the vehicle speed v, are shown as a solid line for the full gas, for 60% gas opening with dashed lines marked with one line and for 40% gas opening with dotted lines and symbols marked with two commas. The gear shift area 2 to 3 is limited by the course P 1, the drive forces P are transmitted by a fixed gear 3 and the drive forces are transmitted by a fixed 4th gear gear.

At the lower gear engaged, the drive torque supplied by the drive wheel 2 is transmitted through the double satellites 6 to the output gearbox, the gearbox reaction member 6 is blocked by the clutch 16 in the housing body 17 against rotation in the opposite direction. The reaction member does not rotate and the centrifugal effect of the auxiliary centrifugal weights 18 is zero. The movement of the auxiliary centrifugal weight 18 in the plane of the folded gear rotation 22 is limited by the contact surface 23 and the adjusting surface 24 of the auxiliary plate 20, the bottom 2% of the recess 21 and the spring-loaded reaction of the gear transmission member 12 which abuts the projection 26 of the reaction member 6. The gear output wheel 3 is connected to the drum 4 of the shift coupler 2, from which the torque is discharged by means of pivot arms 10 hinged on the pegs 4 of the drum 4, to the driver 11 of the output shaft 13 so that the output torque from the gear is formed from; the decomposition between the pivot arm 10 and the driver 11 reversing effect on the centrifugal weight 6 guided in the pivot arm 15 of the pivot arm 10.

Upon increasing the centrifugal effect of the centrifugal weights 2 and the oscillating shafts 10 at the speed of the vehicle V1, varying with the pull according to the pp so that they overcome the reversing forces from the decomposition of the torque forces exiting the transfer to the force bending mechanism, dd ^ the progressive shifting of the associated driving force by the coupling of the reaction member of the transmission and the drum by the coupling 2 by imparting a centrifugal force of the oscillating shells 10 of the centrifugal weights 2 to the lamellae 1 via a controlled shingle 14 at a speed v2 at which the shifting clutch transfers the just-differential torque, the freewheel clutch 14 and the reaction member 6 are released at a speed up to complete connection with the output wheel J-3, 196845, at the speed of the engine during the rotation of the reaction member 6, the centrifugal force of the auxiliary centrifugal weights 18 acts on auxiliary contact area 23 the slats 20 so as to increase the thrust force on the slats 1 of the shift clutch 2 by the rotational speed of the nQII reaction member 6 speed. the evil of the motor n " T, the speed n of the output shaft 13 and the speed n < n >

2SU

MU where i is the ratio of transmissions of adjacent gear ratios on which the gear is realized. As a result, the increase in the driving power of the clutch at this stage of shifting is not merely the speed of the vehicle. In order to avoid the theoretical velocity curve of the forward driving forces F1, the speed of the motor, and the speed of the reaction element 6 towards the lower speed of the vehicle, this would in effect lead to an instantaneous engine revolutions from nMk and revolutions. the reaction member 6, accompanied by a shock in the driving group, and it was not necessary to subtract the vehicle speed from the ramp of the shifting smoothness near the velocity of the wild weights x0. clubs XX. χαχια pi cx amjvcuixa v> x x jívíixwoux

O runs along the driving force curve F4, 4 when the engine speed is equalized, and the speed of the reaction member 6 is abruptly connected to the engine and the transmission output shaft 13 is prevented by releasing the spring-loaded reaction 19 which has been overcome by the rotation of the reaction element. Then, at a speed ngg of the reaction member 6, the auxiliary centrifugal weights 18 abut against the abutment surface 24 by means of a non-flame 20, thereby retaining a further increase in the centrifugal force of the auxiliary shelf at the termination of the shifting process. . the 11th phase of the shifting from the speed v9 to v7 of the vehicle to the fixed connection of the centering weights 18. From the speed of the water at the velocity v, the driving force F1 takes place at the speed of the motor speed of the centrifugal weights of the reaction. of member 6 without changing the effects of centrifugal force help18 continuously, parallel to the courses n ^, Mg and F, 11

When shifting at 60% throttle, the speed of the ηθ ^ = n ^ j fixed coupling is closer to ngj. the reaction member only at 40% of the gas opening is the speed of the fixed connection of the ngy = n ^ transmission less than 10 is reached after the fixed connection is then the speed-dependent ending of the shifting, thus releasing the spring-loaded transmission response, the vehicle speed and the different opening gas.

The unwanted force action of the rocker arms 10 on the actuators is prevented by the groove 12 of the drum 4 ·

Claims (1)

SUMMARY OF THE INVENTION A planetary automatic gearbox with centrifugal shifting clutches provided with power return metering mechanism and centrifugal auxiliary weights carried by the transmission reaction member, characterized in that the auxiliary centrifugal weights (18) are in the space limited by the contact surface (23) and the auxiliary plate (24). (20), the bottom (25) of the recess (21), and the cushioning reaction (19) of the transfer member (6), the cushioning reaction (19) being supported by a protrusion (26) of the transfer reaction member (6).