WO1990001128A1

WO1990001128A1 - Automatically operating gear mechanism

Info

Publication number: WO1990001128A1
Application number: PCT/SE1989/000408
Authority: WO
Inventors: Bengt Erland Ilon
Original assignee: Ilon B E
Priority date: 1988-07-18
Filing date: 1989-07-17
Publication date: 1990-02-08
Also published as: SE459825B; SE8802661D0

Abstract

The present invention relates to an automatically operating gear mechanism, wherein varying speed ratios between a driving shaft (1) and a driven shaft (2) are obtained via a rotor (3) which is rotated by the driving shaft (1) about an axis of rotation (4) and which has weights (5) that are excentrically mounted relative to axes of rotation (6) about which they are provided to rotate, whereby said weights (5), by the rotation of the rotor (3), circle about the axis of rotation (4) of the rotor (3) and whereby the rotational movements of the weights (5) about their axes of rotation (6) are transmitted to the driven shaft (2) via a toothed transmission gear (7). For e.g. eliminating substantial effect limitations in such a gear mechanism or device, the axis of rotation (6) about which each weight (5) rotates, extends at a right angle (α) or at a substantially right angle (α) relative to the axis of rotation (4) of the rotor (3), whereby the mass of the weights (5) twice per revolution is diposed farther away from the axis of rotation (4) of the rotor (3) than otherwise, so that the force generated by the rotation of the weights (5) culminates twice per revolution.

Description

Automatically operating gear mechanism.

The present invention relates to an automatically operating gear mechanism, wherein varying speed ratios between a driving shaft and a driven shaft are obtained via a rotor which is rotated by the driving shaft about an axis of rotation and which has weights that are ex- centrically mounted relative to axes of rotation about which they are provided to rotate, whereby said weights, by the rotation of the rotor, circle about the axis of rotation of the rotor and whereby the rotational move- ments of the weights about their axes of rotation are transmitted to the driven shaft via a toothed trans¬ mission gear.

In automatically operating devices of the above type, the weights rotate about axes of rotation which are parallel with the axis of rotation of the^' rotor.

In such a construction, the moment of each weight will culminate only once per revolution, which provides a power limitation which can be eliminated only by in¬ creasing the speed of rotation of the weights. Addi- tionally, each weight will pass an inner position and an outer position during each revolution, whereby the outer position is at a substantially larger distance from the axis of rotation of the rotor than the inner position. This means that the weights generate power- ful vibrations, which is often disadvantageous. A furt¬ her drawback in devices of the abovementioned type is that the extensive in- and outwardly directed, reversed motions of the weights require much space in radial di¬ rection relative to the rotor axis, which means that the device must have a considerable width to permit the movement of the weights.

The object of the present invention is to eliminate the above drawbacks at a device of the initially de¬ fined type and thus, to increase the efficiency of the device, reduce the vibrations therein, improve its security factor and reduce its width. This is arrived at according to the invention, while the device, or gear mechanism, has been given the characterizing features of claim 1.

While the axes of rotation about which the weights rotate, extend perpendicularly or substantially perpendi¬ cular to the axis of rotation of the rotor, the force generated by the weights by the rotation of the weights about their axes of rotation will culminate twice per revolution. The invention will be further described below with reference to the accompanying drawings, in which fig. 1 is a side view, partly in section, of a device according to the invention; fig. 2 is a view along the line II-II in fig. 1; fig- 3 is a side view of an alternative embodi¬ ment of the device according to the invention; fig. 4 is a section through the device of fig. 3; fig. 5 is a side view of a second alternative of the device of the invention; and fig- 6 is a side view, partly in section, of a de¬ vice according to the invention designed as a clutch, an automatic gearbox, a differential and a differential block for vehicles.

The automatically operating gear mechanism schema- tically illustrated in fig. 1 provides preferably conti¬ nuously varying speed ratios between a driving means 1 and a driven means 2, whereby said means 1, 2 e.g. may consist of a driving shaft and a driven shaft. This is accomplished via a rotor 3 which is rotated by the dri- ving shaft 1 about an axis of rotation 4 and which car¬ ries weights 5 that are eccentrically mounted relative to axes of rotation 6 about which said weights are pro¬ vided to rotate. The weights 5 circle about the axis of rotation 4 of the rotor 3 during rotation of said rotor and the rotational movements of the weights about their axes of rotation 6 are transmitted to the driven shaft 2 via a toothed transmission gear 7. At the embodiment of fig. 1, the driving shaft 1 is rotatably mounted in a bearing 8 provided in a frame 9. The axis of rotation 10 of the driving shaft 1 and the axis of rotation 4 of the rotor 3 extend in this case concentrically relative to each other, and with axes of rotation is meant those imaginary lines about which the shaft 1 and the rotor 3 respectively, rotate.

The rotor 3 has a sleeve 11 which via wedge means 12 is wedged up on the driving shaft 1, whereby the sleeve 11 compulsively follow the rotation of said shaft' 1. Four radially outwardly directed arms are provided on the sleeve 11 and extend perpendicular to each other, whereby they together define a symmetrical cross. At the outer end of each arm 13 there is provi- ded a gear wheel 14 forming part of the toothed trans¬ mission gear 7 and said toothed transmission gear 7 is in this case designed as a bevel drive.

On the outer end of the arm 13, outside the gear wheel 14, there is provided a weight 5 which is non- -rotatably connected to the gear wheel 14 or integral therewith. The weight 5 and gear wheel 14 are provided on a bearing sleeve 15 (see fig. 4) which is rotatably mounted on the arm 13. The bearing sleeve 15, weight 5 and gear wheel 14 are held in place by a nut 16 which is screwed onto a threaded end portion 17 of the arm 13. Alternatively, the arm 13 may be rotatably mounted in the sleeve 11, whereby the gear wheel 14 and weight 5 may be non-rotatably mounted on the arm 13.

The axes of rotation 6 of the weights 5 extend at a right angle °ζ relative to the axis of rotation 4 of the rotor 3 or substantially at a right angle relative to said axis of rotation 4, since smaller deviations from the right angle do not spoil the function of the weights 5. Thus, the angle oC might fall within the range 90 ± 10 but generally, the effect becomes better the closer the angle is to 90 . Through this orienta¬ tion of the axes of rotation of the weights 5 relative to the axis of rotation 4 of the rotor 3, the force generated by the weights 5 by their rotation about their axes of rotation 6 will culminate twice per revolution.

Thus, at the embodiments shown, each weight 5 rota¬ tes such that the eccentric parts 5a thereof relative to its axis of rotation 6, during each revolution, moves away from and towards a point P, wherein the axis of rotation 6 of the weight 5, or an extension thereof, and the axis of rotation 4 of the rotor 3 intersect each other.

This is shown in the drawings in the folloing way: During rotation of the rotor 3 and weights 5, a center line C extending through the axes of rotation 6 of the weights 5 and along the weights 5 will momenta¬ rily run in parallel with the axis of rotation 4 of the rotor 3 twice per revolution. As is apparent from fig. 1, the weight 5 will thereby once be in a position A direc¬ ted to the left from its axis of rotation 6 (solid lines) and once in a position B directed to the right from its axis of rotation 6 (broken lines). The weight 5 will also momentarily be in positions D and E at which the line C extends perpendicularly to the axis of rotation 4 of the rotor 3 (the weight shown with broken lines in this position). In said first position A a point outermost on the weight 5 and the line C is de'signated with PI. In the second position B, the same point is designated P2 and in the third position the point is designated P3. The points PI, P2 and P3 are also shown in fig. 1, where the weights are shown in positions A, B and D (in position F, the point is designated P4) . Hereby, it is apparent that when the weight e.g. rota- tes according to arrow E in fig. 1 (from position D to position A) , the position P3 of the point moves to PI and the distance P3P ⁽see fig. 2) between the points P3 and P decreases to a distance PIP between the points PI and P and increases thereafter when the weight 5 moves further from position A towards position F. When the weight 5 then moves from position F towards posi¬ tion B, the distance from point P2 to point P decreases and then increases when the weight 5 moves from posi¬ tion B towards position D. The gear wheel 14 meshes with a gear wheel 18 in the form of a crown wheel in the toothed transmission gear 7, said crown wheel being mounted on a bearing sleeve 19 which in turn is rotatably mounted on an extension 20 of the driving shaft 1. This construction permits utilization of present parts for mounting the gear wheel 18, however without transmitting the rotational movement of the driving shaft 1 to the gear wheel 18 or vice versa. The gear wheel 18 is here built together with the driven shaft 2, which is formed as a belt pulley for a driving belt .(not shown). The unit 18, 19, 20 is kept in place by means of a nut 21 which is screwed onto a threaded part of the extension 20. The gear wheel 18 and the driven shaf 2 may alternatively consist of two separate members which are non-rotatably connected to each other and if there is a belt pulley, said pulley may also be a separate mem¬ ber which is non-rotatably connected to the driven shaft 2.

Since the rotor 3 has been given the abovementioned shape, the mass of the weights 5 will be found farther away from the axis of rotation 4 of the rotor 3 twice per revolution than otherwise, whereby the force generated by the rotation of the weights 5 about their axes of rota¬ tion 6 culminates twice per revolution. Furthermore, the weights 5 are dimensioned such that they are brought to a stop when the speed of rotation of the rotor 3 about its axis of rotation 4 reaches a certain value, where¬ by said rotary speed of the rotor 3 about its axis of rotation 4 and the rotary speed of the driven means 2 are the same. In the embodiment of figs. 3 and 4, many members are identical or similar to the members of the embodi¬ ment of figs. 1 and 2, and these members have therefore the same reference numerals. The embodiment of figs. 3 and 4 differs from the previously described embodiment in that the gear wheels 14 in the toothed transmission gear 7 is affected by the driving shaft 1 via a gear wheel 22 instead of being influenced through the arms 13. Thus, a sleeve 23 is wedged up on the driving shaft 1, wherebv the sleeve 23 rotates with the shaft 1. The sleeve 23 operates the gear wheel 22 which is designed as a crown or face wheel which either is made integral with the sleeve 23 or is non-rotatably connected thereto. The gear wheel 22 meshes with the gear wheel 14 of the toothed transmission gear 7 and the arms 13 are in this case mounted in a bearing 24 which is rotatably mounted on the sleeve 23, whereby said arms 13 may rotate rela¬ tive to said sleeve 23. As to the rest, this embodiment corresponds with the embodiment of figs. 1 and 2. In the embodiment of fig. 5, the gear wheel 18 of the toothed transmission gear 7 is not rigidly connec¬ ted to the driven shaft 2, but a spring means 25 is provided between the gear wheel 18 and the shaft 2 for resilient transmission of force from said gear wheel 18 and said shaft 2. With the spring means 25, e.g. a coil spring threaded on the extension 20 of the driving shaft 1, vibrations emanating from the gear wheel 18 can be damped such that they are not transmitted to the driven shaft 2, at least not to full extent. The devices described above operate as follows: At an initial stage, the driving shaft 1 rotates the rotor 3 about its axis of rotation 4. At the same time, the weights 5 rotate about their axes of rotation 6, but the driven gear wheel 18 of the toothed transmis- sion gear 7 does not move if the driven shaft 2 is loa¬ ded or braked. When the speed of rotation of the driving shaft 1 has increased to a certain limit and the speed of rotation of the weights 5 has increased correspon¬ dingly, the gear wheels 14, because ofthe increased iner- tia and rotational speed of the weights 5, will execute a rotational moment on the driven gear wheel 18 such that this gear wheel and thereby, the driven shaft 2, starts rotating. The inertia and centrifugal force of the weights 5 culminate twice per revolution and when the speed of rotation of the driving shaft 1 increases, the gear wheels 14 also successively increase their rotational moment on the driven gear wheel 18, which means that the rotational speed of the gear wheel 18 and thus, of the driven shaft 2 increases successively. This is continued until the speed of rotation of the driving shaft 1 has reached a certain higher limit and the rotor 3 reached such a rotational speed that the weights 5 no longer can rotate about their axes of rotation 6, but instead attain positions D or F (see fig. 3). Since the weights 5 no longer can rotate about their axes of rotation 6, the driving shaft 1 and the driven shaft 2 rotate with the same speed. When the load on the driven shaft 2 becomes so high that the driving and driven shafts 1 , 2 no longer can maintain the same rotational speed, the weights 5 and their gear wheels 14 once again start to rotate. Hereby, the force required for rotating the driven shaft 2 is variably transmitted.

Common to the three embodiments of the invention shown is that when the part 5a disposed eccentrically relative to the axes of rotation 6 of the weights 5 in one weight has a certain position within a revolution, the parts 5a of the other weights 5 occupy corresponding positions within their revolutions. This means that when the eccentric part 5a during a revolution about the axis or rotation 6 e.g. is in position A (see fig. 3), the eccentric parts 5a of the other weights 5 occupy corre- sponding positions A within their revolutions.

Common to the three embodiments shown is also that the axes of rotation of all the weights 5 are positioned in a common plane H (see fig. 4) or substantially in a common plane H which extends at a right angle or sub- stantially at a right angle relative to the axis of rotation of the rotor 3. Although it is possible to arrange the weights 5 such that their axes of rotation 6 are in different such planes, such a construction becomes less compact . The weights 5 are preferably arranged relative to their axes of rotation such that they rotate in a plane K (see fig. 4) which extends at a right angle or a sub¬ stantially right angle relative to the axes of rotation 6 of the weights 5 . It is possible however, to provide and/or design the weights 5 such that they rotate in planes with different positions.

In the embodiment shown, the weights 5 consist of substantially planar eccentric discs, but other designs are of course usable. Furthermore, each weight 5 may be designed such that the length of its eccentric part 5a may be varied. Hereby, the rotational moment of the weights 5 may vary and this might occur automatically.

For obtaining a compact design, the weights 5 are provided immediately beside the gear wheels 14 and thus, immediately outside the gear wheel 18 and in the embodi¬ ment of figs. 3 and 4, immediately outside the gear wheels 18 and 22.

The invention is not limited to the three embodi- ments shown, but may vary within the scope of the following claims.

As examples of additional, not illustrated embodi¬ ments one can mention a rotor with only one weight, two, three, five or another suitable number of weights co p- lete with arms or corresponding brackets.

In the embodiment described above, all weights ex¬ tend in the same direction out from their axes of rotation within their revolutions. It is possible however, to pro¬ vide the weights so that they are not directed in the same way, but may be angularly displaced relative to each other within their revolutions. Instead of a center line for all the weights simultaneously passing through e.g. the plane H during rotation, the weights may thus be angularly displaced such that their center lines do not simultaneously pass through the plane H during rotation.

The gear mechanism described above operates e.g. as an infinitely variable toothed transmission gear with gear wheels in constant mesh. Furthermore, the gear mechanism described is e.g. preferably usable as a mecha- nical, frictionless automatic gearbox for vehicles, as a variator for industrial machines, as a frictionless clutc as an endurance and/or long-term brake, as an alternative to differentials (one gear for each wheel), as a device for all-wheel operation on vehicles, as a distributing brake for spring-loaded cable reels or as other devices in other areas.

In the gear mechanism of fig. 6, the abovementioned and in previous figures illustrated system is utilized in vehicles. This gear mechanism includes a rigid outer housing 26 in which two driven means in the form of two outgoing driving shafts 27, 28 are mounted for driving the drive wheels (not shown) of the vehicle. A driving means in the form of a driving shaft 29 from the drive aggregate (not shown) of the vehicle is also mounted in the housing 26. The driving means 29 has a bevel gear wheel 30 which meshes with a gear ring 31. This gear ring 31 is non-rotatably connected with an inner housing 32 which in turn encloses the rotors 3. The inner housing 32 is rotatable about the axis of rotation 4, which in this case also is a common axis of rotation for the two rotors 3. The parts and members of the above device are dimensioned to allow coupling and shifting function between the drive aggregate and drive wheels of the ve- hide. This shifting function occurs at a moderate in¬ crease of the rotational speed of the driving means 29 from idling RPM or no-load speed. At this moderate in¬ crease of the rotational speed of the driving means 29, the rotational speed of the weights 5 also increase and thereby, their resistance against continued increase of their own rotational speed. Thereby, gear wheels 18 are brought to faster and faster follow the rotation of the rotor 3 about its axis of rotation 4. At a continued increase of the operating or drivning RPM of the driving means 29 as well as of the housing 32, the weights 5 show an increased difficulty in having an own rotation about their respective axis of rotation 6 and are finally brought to a stop. Hereby, the rotational speed of the inner housing 32, the accompanying rotor 3 and the out- going driving shafts 27, 28. When shifting down, the abovementioned function occurs in reversed order. At each separate occasion during this shifting function, a balance is obtained between RPM and rotational moment of the driving and driven means 29 and 27, 28 respectively. As a consequence of that the inner housing 32 is common for the two identical rotors 3, of which in turn each is connected to a driving shaft 27, 28, said two driving shafts 27, 28 will have the same speed. But if the load at e.g. rounding of curves is different regar¬ ding the rotational moment or RPM, this is automatically compensated while the weights of one rotor 3 change RPM relative to the weights in the other rotor. This means that the device has a differential function. If one of the drive wheels of the vehicle supposedly looses its grip on the ground, the other drive wheel does not change RPM or rotational moment, since each rotor 3 operates as a separate coupling and shifting unit. This means that the illustrated device also func- tions as a differential lock.

Thus, the device of fig. 6 operates as a clutch, automatic gearbox, differential and differential lock. The details and components of the device may vary and it may be suitable to mount the arms 13 of the rotors 3 at their inner end portions 13a as well as at their outer end portions 13b at the center axis 33 and the inner housing 32 respectively.

It is of course possible to provide more than two rotors 3 and correspondingly more driven shafts, e.g. in cross-country vehicles.

The abovementioned devices also provides an automa¬ tic moment limiting function, since the components inclu¬ ded therein are intended to provide a certain maximum effect and every attempt to substantially exceed this effect is limited by an "inner slipping" because the weights 5 again start to rotate after having stood still at the calculated maximum effect.

The driving means may consist of one or more driving shafts or other suitable elements and the driven means may consist of one or more driven shafts or other sui¬ table elements.

Claims

Claims :

1. Automatically operating gear mechanism, wherein varying speed ratios between a driving shaft (1) and a driven shaft (2) are obtained via a rotor (3) which is rotated by the driving shaft (1) about an axis of rotation (4) and which has weights (5) that are excen- trically mounted relative to axes of rotation (6) about which they are provided to rotate, whereby said weights (5), by the rotation of the rotor (3), circle about the axis of rotation (4) of the rotor (3) and whereby the rotational movements of the weights (5) about their axes of rotation (6) are transmitted to the driven shaft (2) via a toothed transmission gear (7), c h a r a c ¬ t e r i z e d i n that the axis of rotation (6) about which each weight (5) rotates extends at a right angle ( <X ) or at a substantially right angle ( - ) rela¬ tive to the axis of rotation (4) of the rotor (3), ^here¬ by the mass of the weights (5) twice per revolution is disposed farther away from the axis of rotation (4) of the rotor (3) than otherwise, so that the force gene- rated by the rotation of the weights (5) culminates twice per revolution.

2. Gear mechanism according to claim 1, c h a ¬ r a c t e r i z e d i n that the weights (5) are di¬ mensioned such that they are brought to a stop when the rotational speed of the rotor (3) about its axis of rotation (4) reaches a certain value.

3. Gear mechanism according to claim 1 or 2, c h a r a c t e r i z e d i n that eccentric parts (5a) of each weight (5), relative to the axis of rota- tion (6) thereof, twice during each revolution moves away from and towards a point (P) at which the axis of rotation (6) of the weight (5) or an extension thereof and the axis of rotation (4) of the rotor (3) intersect each other.

4. Gear mechanism according to any preceding claim, c h a r a c t e r i z e d i n that the axes of rota¬ tion (6) of all the weights (5) are in a common plane (H) or substantially in a common plane (H) extending perpendicularly to or substantially perpendicular to the axis of rotation (4) of the rotor (3).

5. Gear mechanism according to any preceding claim, c h a r a c t e r i z e d i n that the weights (5) are disposed relative to their axes of rotation (6) such that they rotate in a plane (K) extending perpen¬ dicularly to or substantially perpendicular to the axes of rotation (6) of the weights (5).

6. Gear mechanism according to any preceding claim, c h a r a c t e r i z e d i n that the toothed trans¬ mission gear (7) is a bevel drive having gear wheels (14) which are non-rotatably connected to the weights (5) and centered with the axes of rotation (6) of the weights (5), and which mesh with a driven gear wheel

(18) cooperating with the driven means (2) and centered with the axis of rotation (4) of the rotor (3).

7. Gear mechanism according to any preceding claim, c h a r a c t e r i z e d i n that the rotor (3) has a gear wheel (22) which is non-rotatably connected to the driving means (1) and centered with the axis of ro¬ tation (4) of the rotor (3), and which meshes with gear wheels (14) which are non-rotatably connected, to the weights (5) and centered with the axes of rotation (6) of the weights (5).

8. Gear mechanism according to any preceding claim, c h a r a c t e r i z e d i n that a spring means (25) is provided between the toothed transmission gear (7) and the driven means (2) for resilient transmission of power from the toothed transmission gear (7) to the driven means (2).

9. Gear mechanism according to any preceding claim, c h a r a c t e r i z e d i n that the weights (5) are arranged such that when a relative to the axes of rotation (6^"> of t-he weights (5) eccentric part (5a) of one of said weights (5) is in a certain position (e.g. position A) within a revolution, the eccentric parts (5a) of all the other weights are in corresponding posi¬ tions within their revolutions.

10. Gear mechanism according to any preceding claim and designed for vehicle operation, c h a r a c t e ¬ r i z e d i n that the driving means (1) is driven by the drive aggregate of the vehicle and provided to operate at least two rotors (3), of which each coopera¬ tes with a driving shaft (27, 28) for operating a vehicle wheel, whereby parts and members forming part of the device or gear mechanism are dimensioned to permit coup¬ ling and shifting operation between the drive aggre- gate and drive wheels of the vehicle, whereby the drive shafts (27, 28) start to rotate first when the driving means (1) has increased its rotational speed from idling RPM to operating RPM, and differential operation to enable rounding of curves and driving on bumpy grounds while the driving shafts (27, 28) for the wheels can adapt their RPM with regard to the unrolling distance of the wheels, whereby outer resistance on one of the vehicle wheels can not affect that wheel or the other wheels with regard to RPM and rotational moment.

11. Gear mechanism according to claim 10, c h a ¬ r a c t e r i z e d i n that one rotor (3) is desig¬ ned and dimentioned as the other rotor (3) and that both rotors (3) in the driving means (29) are given the same rotational speed, whereby different loads on the driving shafts are automatically compensated in that the weights (5) of one rotor (3) change their speed of rotation relative to the rotational speed of the weights (5) of the other rotor (3), whereby the device or gear mecha¬ nism permits differential operation.

12. Gear mechanism according to claim 10 or 11, c h a r a c t e r i z e d i n that the rotors (3) are operated in pairs by a common driving means (1).

13. Gear mechanism according to any of claims 10-12, c h a r a c t e r i z e d i n that the rotors (3) are mounted in a common housing (32) wherein arms (13) forming parts of the rotors (3) and provided with the weights (5) are mounted with their inner end portions (13a) as well as outer end portions (13b).