BG97786A - Hydromechanical stepless gear box - Google Patents

Abstract

The gear box can be used basically in the automobile industry. It has a simplified design and reduced cost. It performs STEEPLES two-way transmission of a changing torque in front drive and its one-way constant transmission in reverse drive, smooth change-over and stepless change in front drive of the transmitted torque and sufficiently big range between the maximum and minimum gear ratio. The gear box includes a pump (12) of a hydrotransformer, connected, on one side across a clutch (8) to a shaft (4) carrying a small central gear (12) of the double planetary mechanism, and - on the other side - across the shaft (7) of turbine (1) on the hydrotransformer - to a second central gear (14) of the same double planetary mechanism. The two central gears (12 & 14) are coaxially positioned and have the same number of idler gears (10 & 13). Each of the central gears (12 & 14) is meshed to the idler gear of the other group which is under/above it, the idler gears (10) of the big central gear (14) being also meshed to one crown wheel (11) fitted to the outgoing shaft (15) of the box. The axes of the two series of idler gears are fixed to a common guide (17) connected to mechanism (9) locking or freeing the guide (17) to/ftom the housing (16) of the box.

Description

(57) The gearbox can be used mainly in the automotive industry. It has a simplified construction and reduced cost. It performs a two-step stepless transfer of forward-rotating torque and one-stream constant reverse-reverse, smooth start and stepless forward torque transmission and a sufficiently large range between maximum and minimum transfer ratios. The gearbox includes a pump (12) of a hydraulic transformer connected, first, through a lamellar clutch (8) to a shaft (4) carrying one small central gear (12) of the twin planetary gear, and on the other through the shaft (7). of the turbine (1) of the hydraulic transformer with a second large central gear (14) of the same dual planetary gear. The two central gears (12 and 14) are coaxially arranged and have the same number of satellite gears (10 and 13). Each of the wheels (12 and 14) is engaged by a satellite gear below or above it in the other group, the satellite gears (10) of the large central wheel (14) being engaged and a crown (11) attached. for the output shaft (15) of the box. The axes of both sets of satellite gears are fixed to one common carrier (17) connected to a mechanism (9) that locks or releases it to / from the housing (16) of the box.

claim, 2 figures HIDROCHAM B1? CTSEBHHA <5FQ? 0Cm K7IA Boris Georgiev Macedonian, Gennady! Borisov Takov, Lubomir. Georgiev 1ikolov, Tihomir Borisov Takov - Sofia, Bulgarian

The present invention relates to a hydromechanical gearbox, which will find application in transport mothers, and particularly in the automotive industry.

There are various designs for automatic, hydromechanical gearboxes that have been used in the automotive industry. • The bulls have been created based on a combination of a hydraulic transformer, pe.cn · hydraulic clutch and planetary mechanisms.

1of one of the first structures of this type to be used in the automotive industry is the gearbox, known under the trade name Hydramatic. / 1 / However, the Sata is a relatively complicated one, consisting of many components and elements of structural renegade. Thus, in its circuit design provides a hydraulic clutch and three planetary mechanisms coaxially arranged one after the other, with concentrically located one in other shafts, the central inner shaft is the turbine, and it is dense, with the first two planetary mechanisms braking gears are provided, and a locking mechanism is provided for the third planetary mechanism intended for reverse operation only. In addition, since this gearbox is a power train, you are also provided with a gearbox for the individual gears realized in the four speeds: for which the gearbox is read.

One newer technical strap in this area is the automatic transmission used in Mercedes cars since the 1980s. / 8 / Sata is a combination of a hydrotransformer and one is a dual planetary mechanism is a two lamella clutch and three left-brake mechanisms, since, however, it is a stepwise one, it provides for a complex hydraulic command system for controlling individual speeds:

Stepless hydromechanical gearboxes are also known. Of this type, for example, gearboxes Diaiaflow and Turbouleid ·, / I / This type of boxes, however, to provide a sufficiently large range of transmitted torque, I had in my zplneneye more than one hydrotransformer, which complicates the construction of pits and increases their cost, 8 of the invention is to create such a hydromechanical stepless gearbox that is structurally simplified, with easy operation and reduced cost, with guaranteed: smooth start-up, stepless change Output transmissions torque and enough voluntary range between maximum and minimum Transfer otioienie,

The purpose is to provide a combination of a hydrotransformer, a twin planetary mechanism, a lamella clutch, and a lock: a mechanism interconnected functionally in such a way as to provide a steady, two-way forward torque transmission and a single-stream constant forward transmission of the same stroke, two-torque torque is transmitted in parallel through the turbine and the pump of the torque converter, and the one-stream only through the turbine of the torque converter,

Thus, according to the present invention, the pump of the hydrotransformer is connected on one side, through its hollow shaft and through one lamella clutch, is one, fixed on the narrowly hollow shaft of the lamella clutch, the first smaller central gear wheel of the twin planetary mechanism, and on the other hand, through a turbine; of the torque converter and through its shaft coaxially 'J within the coaxially arranged hollow shafts of the solder and the lamella clutch, with a second, more preferred central gear than the twin planetary mechanism · further, the second larger central gear is engaged with one triple satellite gears, having a significantly increased length of teeth compared to that of the two centers: _w gears · This length is tailored to their ability to be engaged on each side of the central axis of symmetry , additionally with another gear wheel from another gear wheel with a length of teeth equal to that of the first <less central gear wheel on which that gear wheel 3. are satellite.

The axes of the two satellite gear wheels are fixedly fixed to a single guide wheel connected to a mechanism that locks or releases the drive to / from the housing of the box.

Finally, the triple satellite sprocket with enlarged teeth * is pinched externally by a crown gear, which transmits the movement of the output shaft.

With the so-called hydromechanical stepless speed; box, after the pump of the chndrotransformer is driven by the motor included therein, the following is realized:

- When the lamella clutch is switched on and the locking mechanism is switched off - the freewheel starting and forward movement is a two-way transfer of the rotate ie once from the pump, in sequence *

- 4 heavy through the lamellar clutch, the first less central gear <, two triple-meshed satellite gears and the gear wheel, to the gearbox output shaft, respectively, and second, from the feeder in series through the hydrotransformer turbine, the turbine shaft, the second larger center gear, the triple of its satellite gears with increased tooth length and the crown, to the outlet sting of the box.

- With the clutch disc off and the non-drive brakes switched on - smooth starting and reversing, with one-torque transfer of torque from the pump, sequentially through the turbine and its shaft, the second larger central gear wheel, the triple of its satellite gear wheels with enlarged gears to the teeth and through the gear wheel to the gearbox output shaft.

The schematic embodiment thus presented, and the stepless hydromechanical gearbox, provides the aforementioned positive features while avoiding the complex hydropneumatic control devices of the various modes of wall hydromechanical gearboxes, and further has the advantage of using known components and components technological gaps, which logically leads to reduced design, production and operating costs.

To further elucidate the object of the invention, an exemplary embodiment of the same is attached herewith in accordance with the foregoing drawings, where:

- Figure I is a schematic view of the hydromechanical stepless gearbox according to line AB-C of FIG. 2;

Figure 5 is a schematic front view of the mechanical part of the gearbox depicting the twin planetary pebble, viewed in the direction of line D-1 of FIG.

As can be seen from the attached figure I, the hydromechanical stepless gearbox contains a standard-type hydraulic transformer constructed by turbine wheel I and pump 2, which pump 2, together with housing 3 and turbine I, is driven by an external motor 5 · (Figure I does not indicate the stator of the hydraulic transformer, since it is irrelevant for further exposure). The shaft 4 of the pump 2 is hollow and is connected to one joint - thereon, the same hollow shaft 6, through one lamellar joints. At the end of the second coaxially arranged hollow shaft b, one first, smaller central gear 12 is mounted, with normal length ηϊ teeth, It in turn is engaged by a triple of its satellite gears 13, also with normal tooth length.

On the other hand, the turbine shaft 7 is coaxially arranged in the coaxially arranged hollow shafts 4 and 6, extends beyond the shaft 6, with a second, larger central gear wheel 14, also with a normal tooth length, fitted at the end thereof. - a large central gear wheel 14 is engaged by a second triple satellite gear wheel 10, which has an extended tooth length, with charcoal; each of these satellite wheels 10 can also be rearranged by the satellite wheel 13 lying underneath its satellite wheel 13 of the small central gear 12, which is a group of small centers with three satellite wheels 13 disposed in front of the larger central gear 14 in direction to hydrotransformer fertilizer.

The axes of the two satellite gears 10 and 13 are fixed to one guide member 17, connected to the locking mechanism 9, the fixed part of which is fixed to the housing 16 of the box, and the carrier 17 is freely camped 18 on the hollow axis C with the small central gear 12.

The satellite gears 10 themselves, with increased length of the teeth, are engaged externally by a crown gear II, fixed to the output shaft 15 of the gearbox.

The relative position of all the gears in plan is shown in Figure 2. _.

The construction described in this way is as follows:

- Cree idle; in this case the lamella clutch 8 and the locking mechanism 9 are switched off. Then, the motor 5 rotates the casing 3 and the pump 2 of the torque converter. The pump cannot transmit its rotational motion through its hollow shaft 4 further, because the blade 8 is switched off. Therefore, the movement of the movement along this mechanical path is not realized. However, as the speed of the pump 2 increases, as a result of the centrifugal forces, the oil contained in the torque converter forms a cylindrical flow, directing from the pump 2 to the turbine I, hitting its blades and rotating it. The rotation of the turbine I is transmitted through its shaft 7 to the larger second central gear wheel 14. The latter in turn rotates its satellite three gears 10 with increased tooth length, and they, the other three satellite satellite gears 13 with the normal length of gear. and from there, the first w smaller gear wheel 12 and the associated portion of the non-engaged lamellar clutch 8. As the locking mechanism 2 is released, i.e., the guide 17 is not engaged with the axes of the two satellite threads fixed to it. gears 10 and 1 3, rotates freely together with the satellite gear wheels 10 and 13. Thus, the satellite gear triple 10 with increased tooth length cannot transmit the rotary motion of the crown wheel II, so that the output shaft 13 remains at rest again .

- Erie forward movement; in this case, the lamella® clutch 8 is engaged and the locking mechanism 9 is off. Now, as the pump 2 is driven, its shaft 4, through the engaged clutch 8, drives the shaft 6 with the first, first, smaller gear wheel fixed to one movement 12. The movement of that small first central gear 12 through the two triple satellite gears wheels 13 and 10 are transmitted to the second inner gear wheel 14, which receives a rotational direction opposite to that of the small gear wheel 12. Since the large central gear 14 is fixed to the turbine shaft 7 of the hydraulic transformer, it and the turbine I rotates in a direction opposite to the direction of rotation of the ion 2. In this position, the crown gear II and the output shaft 15 remain stationary. Further, with increasing pump speed 2, by the specified transfer of rotational motion, the turbine speed I also increased, This leads to an increase in the difference in their angular rotational speed to the moment when pump 2 hydraulically becomes operational. Turbine stop I. 1 result Turbine speed j

- 8 start to decrease until full stop λ is reached, »» then start rotation 1 in the direction of rotation of the pump which continues until their speed is equal; For its part, the larger central gear 14 connected to the turbine shaft 7 also decreases its rotation to a stop and then reverses the direction of rotation with a subsequent increase in speed until they align with those of the pump. The summed rotational motion of the two central gears G2, and 14, through the three triangles satellite gears 1: 3 and 10, is transmitted to the crown gear II, respectively to the output shaft 15, which smoothly reaches the pump speed, respectively .of the engine.

- Reverse motion; in this case, the lamella clutch 8 is switched off and the locking mechanism 9 is engaged. The rotational motion of pump 2 is mechanically transmitted only to the clutch 8. As it is switched off, the torque transfer is interrupted here. The second mode of motion transfer is realized by the pump 2, at sufficiently high speeds of the same, through the turbine I, the turbine shaft 7, the large central gear 14, the triple satellite gears 10 with increased tooth length and the crown gear II, output shaft 15. The satellite gear wheel triple 10 rotates crown II in a direction opposite to the direction of rotation of the large central gear wheel 14. At the same time, the other satellite gear wheel 13 of the small central gear wheel IB rotates the last parasite. o, and this rotation is transmitted to the exceptions plate clutch 8, wherein the interrupt.

Thus, in reverse, the transmitted torque is approximately constant insofar as it is mainly dependent on the gear ratio of the planetary mechanism and to a lesser extent on the torque change in the torque converter. Conversely, the forward movement due to the specific coupling between the elements of the hydrotransformer and the planetary mechanism according to the proposed two-torque torque transfer scheme ensures smooth starting and transfer to the output shaft of a changing torque depending on the needs.

Parking; engine They are switched off and both the lamellar clutch 8 and the locking mechanism 91 are switched on. Thus, the engine'through the pump 2, its shaft 4, the lamellar clutch 8, its shaft b, the small central gear 12, respectively, the three triple satellite gears 13 and 10 and the crown gear II, are directly and rigidly connected to the output shaft 15.

From the foregoing, it is evident that in the proposed hydromechanical stepless gearbox there is a particularly favorable but specific connection between the hydrotransformer and the used planetary mechanism, realizing an interconnected self-regulating self-regulating system with two-flow torque transfer and forward transmission. the same when reversing, which coupling reveals the properties of the planetary mechanism as an asymmetric differential.

as a result, a smooth start is achieved, a steady change in the forward torque of the transmitted torque in a sufficient range, with a simplified design of the box as a whole, which makes it widely applicable.

Claims (3)

EAT1NM Claims I. I. a hydromechanical stepless gearbox comprising a hydrotransformer and planetary gears in which the axis of symmetry of the planetary gears is aligned with the axes of concentrically disposed, respectively hollow and dense shafts of the pump and the turbine of the hydrotransformer, characterized by that as a clutch, a hydrotransformer is provided, wherein the hollow shaft (4) of its pump (2) is separated by a lamella clutch (8) from a coaxially arranged second hollow shaft (b) with a stationary first mounted thereon. a small central gear wheel (12), constituting an element of a first part of a twin planetary gear, and the outwardly extending hollow shafts (4, b) concentrically located solid shaft (7) and the turbine (I) of the hydrotransformer ends therewith mounted thereon. a second large central gear (14) from a second part of the twin planetary gear (mechanism) connected via its satellite gear wheels (10) and to the fh crown gear wheel (II) with the output shaft (15) of the box, such as these satellite gears / 10 / that are ** enlarged and the length of the teeth are engaged internally, respectively, from the side of the central axis of symmetry, with the satellite gears / 15 / of the small central gear fLZ / from the first part of the planetary mechanism, Hydromechanical stepless gearbox according to claim I, characterized in that the axes of the two satellite gear wheels (13,10) are fixedly fixed to one common guide fl * lf, which is an element of the locking mechanism ($). - II - Hydromechanical stepless gearbox according to claims I and 2, characterized in that the carrier (17), which is an element of the locking mechanism (9), is freely camped (18) on the hollow axis (in) to which the small central a gear wheel (12) of the first part of the coupled planetary mechanism, and is provided with at least one known brake element in its part, which contacts the stationary braking element (9) fixed in the housing (16).