DE1197712B - Epicyclic gear with overload protection - Google Patents

Description

FEDERAL REPUBLIC OF GERMANY

GERMAN

PATENT OFFICE

EDITORIAL

Int. Cl .:

F 06h

German class: 47 h -13

Number: 1197712

File number: H 27577 XU / 47 h

Filing date: July 13, 1956

Opening day: July 29, 1965

The invention relates to a planetary gear with overload protection, in which a lockable Gear part held so resiliently by brake ring parts resiliently supported in both directions of rotation is that it is released when a certain torque is exceeded depending on its rotation will.

Epicyclic gears in connection with brakes or locks are used as safety switches in a wide variety of ways Executions known. The only disadvantage are the only special functions in relation to the effort, especially since the complex planetary gear is only a means to an end. One more or less large number of lever joints or friction pairings, stressed by the transmission forces, are subject to wear that increases play and increases the additional forces, and they hold particularly well not withstand vibration-like stresses in the long run. Drive elements are known in large numbers for securing and switching for only one purpose each, which is provided for the fulfillment Requirements of different brands are often used in combinations that consume space and costs Need to become. They are to be adapted to the circumstances on a case-by-case basis and do not allow either organic unions with the different reductions in each case and still uniform designs or general applications. The striving for small, cheap gearboxes is uniform Structure for a wide variety of applications, which in the case of a universal drive element is the Organic association of high-performance gear reductions that are optimally adaptable to the respective purpose with overload fuses means.

The invention is based on the universal application of an overload protection To enable epicyclic gear for statically and dynamically highly stressed drives.

The invention is based on a known planetary gear transmission with overload protection, in which a lockable gear part through in both directions of rotation resiliently supported brake ring parts is held so resilient that it is exceeded when a specific torque is released depending on its rotation. Such a planetary gear is so perfected according to the invention that the brake ring parts freely movable on all sides and adjustable are guided only on the lockable gear part and a wedge-shaped at their joints Include space in which the cylindrical head of a spring-loaded, pivotable and axially displaceable lever epicyclic gear with overload protection

Applicant:

Fritz Hinze,

Lintorf (District Düsseldorf), Am Kohlenday 27

Named as inventor:

Fritz Hinze, Lintorf (District Düsseldorf)

is brought to bear by springs or hydraulic cylinders that with increasing torque and increasing rotation causes the brake rings to be released.

The invention is explained in more detail on the basis of the following description of exemplary embodiments. It shows

F i g. 1 shows a horizontal cross section through an epicyclic gear according to the invention,

F i g. 2 shows a perpendicular section to FIG. 1,

F i g. 3 shows a detail of FIG. 1,

Fig. 4 is a side view of another holder of the brake ring parts,
F i g. 5 and 6 two details of FIG. 4,

F i g. 7 a manual switch for the brake ring parts,

Fig. 8 to 10 curve shapes for the joints of the brake rings,

11 shows an offset lever for spreading the brake rings,

F i g. 12 a detail of FIG. 2,

F i g. 13 an embodiment of the invention with the brake rings being pressed by pressure medium,

F i g. 14 another drive for the pressure medium pump,

15 shows a horizontal partial cross-section through a further embodiment of the invention,

F i g. 16 a one-piece brake ring,

F i g. 17 a detail of FIG. 16,
18 shows an embodiment of the lever for spreading the brake rings,

19 and 20 show a view and plan view Another embodiment of the lever for spreading the brake rings.

The in Fig. 1 and 2 illustrated epicyclic gears embodies the general principle of the invention. The pinion shaft or input shaft 1 of the

509 628/214

3 4

The gearbox drives the single or multiple existing ones. The arrangement shown works when starting Intermediate gears 2 on, which are on the intermediate shafts 3 of the drive motor in such a way that when it comes up are attached. These intermediate shafts also act as the load during the start-up of such a strong Ver pinion shaft executed, form the planet gears and rotation of the planetary gear carrier 5 occurs that at drive the gear wedged onto the output shaft 7 with a higher reduction than 5 alone already a starting ring gear 4 trained sun gear and are in effect, but in any case the creation of the the revolving gear carrier 5 mounted so that the flying tooth flanks of the wheels goes without impact, seated intermediate gears 2 without further ad- When starting two separate processes can be changed. At the other end are to be distinguished. On the one hand, the approaching one must the intermediate shafts 3 in an attached cage 6 io motor overcome the backlash that at high of the planetary gear carrier 5 stored. Both bearings are reductions by the sum of the games in the are in their dimensions and spacing so on individual levels can have such a high value, matched to each other that an equal load that the engine before overcoming the overall game or service life is present. Furthermore, the storage has already reached full speed or power Listed in the cage 6 so that the ring gear 4 has 15. On the other hand, the motor must have the mass of the anvon the output side from the machine driven by the cage 6 in motion. Are strolling here is required for longer starting times, the

The determination of the Ümlaufräderträgers 5 is with contact pressure for the brake ring parts 8, which by the a brake of a special kind and arrangement is effected in front of piston 17, are gradually generated, taken to the initially mentioned different 20 This can be done, for example, that with to get similar effects. According to Fig. 2, turning on the motor is a pump to work the brake consists of two brake ring parts 8, which begins at the, which gradually end the full contact pressure are provided with approaches 9, so that it testifies to. Such an arrangement is given below A wedge-shaped space is still described at their joints.

close, which narrows radially outwards. In 25 during operation, if the

this space is where the cylindrical head with set torque is an additional

10 a rotating about a fixed pivot bearing 11 of the brake ring parts 8 and beyond

Lever 12. This lever 12 is in the pivot bearing 11 lifting the same, so that the set pivot

longitudinally displaceable and maintained by means of a moment and overloads

Helical spring 13, which on the one hand can be avoided against the torsion 30, regardless of the reasons

bearing 11 and on the other hand towards the end of the lever they occur.

12 is supported, held so that the head 10 in the By this arrangement, the gearbox has the following wedge-shaped space between the lugs 9 of the properties or offers the following options:
Brake ring parts 8 always rests without play. In the two-part design of the brake ring, the levers 35 are 1. Highly elastic shock absorption,
12 is also available twice, so that a syrn- 2. limitation of the torque,
metric arrangement arises. In the same way 3 _{acting as a} starting clutch,
three- and multi-part brake rings can be used with. _AU , _t ° _u · γ «, ι *
corresponding number of levers 12 be available. ⁴ Shutdown in the event of an overload,

When the brake ring parts 8 are rotated, the 40 5. Switching the drive on and off under load

Lever 12 pivoted, and the heads 10 spread the u » ^d while running,

Brake ring parts 8 apart so that the brake 6th acts as a vibration damper,

is more or less ventilated. The levers 12 7. Continuous slip (adjustable),
can at the same time the brake ring parts 8 resilient

secure against rotation. For this purpose 45 The elastic mounting of the brake ring parts 8 the springs 13 must have a strength corresponding to the rotation against rotation to be transmitted, also by means of pressure cylinders. Keep following. Instead of the springs 15 of the brake rings, these cylinders can act against rotation but can also act on the projection 14. A special arrangement may also be made. As in Fig. 2 borrowed to let the cylinder act on the lugs 9, is also shown, the brake ring parts 8 50 so that thereby the brake ring parts at the same time in their center a projection 14 which are held together between two. Instead of compression springs 15, which in turn are held against cylinders, spring pots or other fixed stops 16 of the gearbox housing or similar elastic bodies can also be used,
place. In this case, the springs 13 only need in FIG. 1 is indicated by dash-dotted lines that it is to be strong, that the backlash-free application of the 55 for example the ring gear 4 is provided with a conventional brake lever heads 10 in the wedge-shaped space. This training is used for special parts, for example for crane winches. The brake

The brake ring parts 8 can be used in different ways. The ring gear is the holding brake for the shark held in their intended position. In ten of the load with the engine switched off. In the sense of the F i g. 2 are the lugs 9 at the ends of the brake 60 invention finds a mutual influence of Rings 8 provided with cylindrical bores in the gear brake and the holding brake in the way each of which has a piston 17. The two take place that the holding brake only then releases or closes Pistons are loosened by a common pull rod when the gearbox starts to loosen bound. If pressure medium is let into the cylinder, the engine transmits sufficient torque, so the ends of the brake rings 8 against each other 65 so that a crash of the load cannot occur, pressed. To the passage of the pull rod of the piston so that a through the transmission of the invention 17 is the head 10 of the lever 12 in the middle from squirrel cage motor in crane construction use saved, see Fig. 3.

5 6

Fig.4 shows another possibility of holding double cones. Furthermore, instead of cylindricity of the brake ring parts 8. By longitudinally elastic, on surfaces also flat surfaces with or without conical grooves one end under adjustable spring pressure can be used. Inner straps can also be used 18, which the brake ring parts 8 single or multi-shoe brakes are used, loop around it and fasten it at the other end 5 According to the setting of the holding force results are, the brake ring parts are to be braked for a certain torque to be transmitted The surface is pressed on and elastic against rotation - in all cases a certain deflection of the lever keep. The bands 18 can be steel springs, rubber 12. As in FIG. 12 shows, an adjustable end or Fabric ribbons or according to F i g. 5 ropes or switches 26 can also be provided for when the chains are fully off with switched on elastic bodies 19 io pivoted position of the lever 12 the drive motor be. With this arrangement there is holding power and power off. Should, however, the shutdown with a Contact pressure take place in a certain ratio to a certain inertia or delay, see above each other. a temperature sensor 27 can be attached to the brake ring

According to FIG. 6, the fixed end 20 of the belt 18 parts are provided. The automatic Abschalan the attachment point opposite the other 15 device then takes place when a set point is reached End of 21 offset, whereby the same elasticity of the temperature. This heat-dependent shutdown Belts 18 a greater rotation of the circulation can also be done mechanically by the springs 28 wheel carrier 5 is achievable. for generating the contact pressure via melting

In many cases, switching the ring 29 on and off is effective. These rings 29 melt at a Drive required when the engine is running. 20 certain temperature and have such a thickness, This possibility is also with the device that after melting away the springs 28 entder Invention given as F i g. 7 shows. This is going to be exciting. Lighter springs 34 then lift the the circuit made by hand. The lever 12 ring parts 8 from.

is lengthened and carries a bolt 22, which is applied to the pressure medium.

Ring slot 23 of the control sleeve of a hand lever 24 25 so the release of the brake ring parts 8 by the intervenes. This lever 24 can be pivoted at 25. How out is stored, namely the storage is expediently shown in FIG. 13, is of the one with the engine connected to the fixed pivot bearing 11 of the lever 12, rotating input shaft 1 of the transmission but it can also be provided on the gear housing eccentric 30 driven a piston pump 31, which be. If the hand lever is anticlockwise 30 pressure medium via the pressure line 32 to the cylinder pivoted, so the lever 12 in Figure 7 33 is supplied, whereby the brake ring parts 8 in the ernach pulled to the left, causing the head 10 to act in the braking manner against the action of the spring 34 ring parts 8 spreads and the brake is opened. that are required for the brake to be released By securing the hand lever 24, the pressure medium can be switched off. Of the Brake must be kept off. 35 Line 32 leads a branch 35 to a fixed

Of course, the circuit can also be pivoted by means of the sleeve 36 in which the pivot bearing 11 can be pivoted Threaded spindle and handwheel or on an electrical one. This pivot bearing has an axial path here as well as by pressure medium control. the outlet channel 37, which has two radially extending

The ends of the wedge-shaped space enclosing branch channels 38 is connected, which when pivoting the brake ring parts 8 can be moved to different degrees by the pivot bearing U by a corresponding angle inclined surfaces with sharp or curvilinear with the branch 35 to align, so that Have transitions or the cylinder 33 is relieved in the form of a curve as a whole. This is for pushing as in Fig. 8 to 10 is shown. By doing this, loads apply.

In the pressure line 32 of the pump 31 is for pressure applications be met by the form 45 setting an overflow valve 39 switched on, the of the wedge-shaped space, the holding force and the elasticity via a lever linkage 40 with the lever 12 Twist is appropriately matched that after overcoming a certain the. The head 10 and the surfaces on the lever idle stroke in the linkage 40 the pivoting of the lever ends can also be shaped so that at 12 a reduction in the pressure setting of the ven-work a mutual rolling similar to the 50 tils takes place. With this, the pressing force becomes the braking intervention of teeth takes place in gear systems. ring parts decreased and it occurs in the area of a It is also possible, the head 10 of the lever 12 with certain set torque a very Rollers should be provided so that sliding · * soft lifting and slipping occur in the event of high forces, the given friction to avoid. if there may be permanent slip. Of this

Fig. 11 shows that the pivot bearing 11 of the lever 12 55 can be used in multi-motor drive may be offset to the central position of the lever 12. will.

As a result, a substantial amount of the piston stroke of the pump 31 can be adjusted in one direction of rotation

greater deflection can be obtained without having to set the time when starting, a lifting of the brake ring parts 8 already takes place. For this purpose, the piston rod 41 is on one of the Ex-dies The offset position of the pivot bearing 11 can be driven by adjustment 60 centers, and firmly given birth at the other end be by the pivot bearing 11 on a handlebar 42 supported by it. This will make the Spindles adjustable slide is attached. required for the full application of the brake ring parts 8

The execution of the braking surfaces on the circulation loaned amount of pressure medium in a more or less wheel carrier 5 can be produced in various ways, ie. that is, the tempering period becomes men will be. Regulated apart from the purely cylindrical 65.

Shape of the braking surfaces with one or more In the pressure line 32 is a three-way valve 43

Brakes next to each other can be switched on for arbitrary manual switching surfaces have wedge-shaped grooves or is intended as a whole. When changing this valve, the

7 8

The pressure line is shut off and the cylinder 33 is in turn radially flexible, for example via

ventilates. Tooth couplings, is secured against rotation.

According to FIG. 14 is a pump 44 for the pressure.

Medium funding is provided, the storage centering the planetary gears the possibility of carriers 5 is driven by a cam 45. Give the S, the position of the planet carrier 5, given

for achieving and maintaining the contact pressure through the inevitable tooth system of the wheels 3

force required pressure is here in dependent and 4, adjust. The driving shaft 50 is closed

generated by the slip. This type of pressure- this purpose with the shaft 1 about resilience

generation is preferably appropriate in cases where enabling facilities, such as the a slight permanent slip is necessary. The pump 44 io tooth coupling 51, connected,

can have a fixed or variable stroke. The center bearings of the gearbox only have

In the practical implementation of the invention, axial thrusts from helical gearing can be incorporated, thought it is possible to design a structural design. This ig driving shaft 1 or 50 is omitted.
The advantage is achieved that the space in front of the planet carrier 5 with the pinion of the input shaft 1 and the gear 2 brake disk 46 can be held self-adjusting, but the gearbox for accommodating the brake can also be used by the planet carrier 5 alone is self-turned. Such an embodiment is held in an adjusting manner and the brake disk 46 is shown rigidly in FIG. Here is to be stored with the Umlaufräder- ao. In this case, the brake disc carrier 5 is connected to a lateral brake drum 46, which is used at the same time via, for example, a toothed coupling 59 to support the planet carrier 5 via bearings 47 and 48 in the sense of a self-rotating gear carrier. Connected for maintenance setting of the planet carrier,
the friction surfaces and for assembly are the For enabling permanent slip, the brake ring parts 8 and their holder including 25 NEN the brake ring parts 8 according to the invention so geder lever 12 on the gear cover 49. Hold the connection, be pressed and designed that one of the drive shaft 50 with the pinion shaft 1 is lubricated film formation with practically wear-free via a toothed clutch 51, so that the brake operation is achieved easily. The wedge required for this can be removed. Furthermore, the cover 49 can form a gap in the formation of the support of the brake ring part 8, if the position is appropriate and in order to further facilitate accessibility. Be divided horizontal plane. The replacement of the formation of the wedge gaps and the loading of the brake ring, the pinion shaft 1 and the gear wheel 2 is also possible in the case of the illustrated parts. A large number of brake ring parts 8 can be supported by the construction without difficulty. will.

For the automatic contact of all teeth with more than one 35 The illustrated holder of the brake ring parts 8

Reren intermediate shafts 3 according to FIG. 15 for the purpose of rotation by the lever 12 counteracts

the inevitable participation of all wheels in the contact pressure. But it is also possible to use the parts

For power transmission, the planet carrier 5 is to be designed with or in such a way that holding force and contact pressure

without brake disk 46 act radially resiliently centering in the same direction.

Via devices 57 on bearings 47 and 48 so 40 The illustrated and described transmission design

stored in such a way that the flexibility of the can exceed the set dimension

Planet carrier 5, the teeth of the intermediate shafts 3 in the loads not to. But also internal additional burdens

Create ring gear4 for the proportional power takeover, for example from toothing errors

can. absorbed shock-absorbing. Such transmissions need

The devices 57 can be elastic rings or 45 surfaces therefore not to be designed larger than it Ring pieces made of rubber or plastic or the average load even with intermittent loads elastic metal body, like corrugated spring steel sheet corresponds to mode of operation. In addition to great operational reliability or Coil springs. health and service life with low susceptibility to failure

The same device can also easily and cheaply dismantle such gears on both sides.
Support can also be provided at bearing 58. By 5 ° According to Fi g. 16 is a one-piece brake ring 52 in front of the radially flexible bracket of the planet, which exerts the braking force primarily through its carrier 5 with the levers 12 on the brake rings 8 and the self-adjustment of the planet carrier by springs 53 can also be equipped with pressure. According to the invention, not hindered by its springs, the dental systems. tion, the ring 52 acts like a multi-part ring.

Except for the weights, the forces balance each other out. 55 For an approximately even tension, the

on the one hand, due to the contact with the tooth flanks of the ring 52, a variable cross-section. So that he

Wheels 3 and 4 and, on the other hand, by the opposing forces when releasing as a result of the deflection of the lever 12

forces on the levers 12. To compensate for the fact that it lifts evenly from the brake disc, he has

weight, provided that in relation to the attacking laterally concentric edges 52 a, which are completely

Forces, as well as for a certain centering- 60 open brake against the corresponding stop

In the case of the planetary carrier rotation, apply at the edge54 of the gearbox housing (see Fig.

switched drive, also for the recording et- 17). Such rings 52 are preferably paired

Waiger residual forces from workshop inaccuracies, is wise, offset against each other, one or more times.

the respective gear member to be held is primarily turned.

the planet carrier5 held radially resilient. It 65 Fig. 18 shows an embodiment of the lever 12 as

can also be used together or alone with the protruding leaf spring. This training is already in the

Features the pivot bearing 11 in a ring to the zero position of the lever 12 a corresponding holding force

be mutually immutable, the ring being exerted on the brake ring parts 8.

In Fig. 19 and 20, the lever 12 is fastened on a torsion bar spring 55 which forms the pivot axis of the lever 12 and is fastened in bearings 56 of the transmission housing. Here, too, a holding force is already effective in the zero position.

The elastic holding of the brake ring parts 8 against rotation can also be used as a measuring device for the torque can be used that a mark on the face of the brake rings on one after The calibrated scale is swept past the spring, which lies inside the gear unit through a sight glass can be made visible. The measuring device can also be transmitted externally by suitable transmission of the transmission, it can also be used for control purposes by various known means can be used, for example, by actuating the setting tool of a continuously variable transmission.

Instead of braking the planetary gear carrier 5, the brake ring parts 8 can also move onto another rotating one Act part of the planetary gear, for example on the ring gear 4 according to FIG. 1, where then the output shaft 7 is to be connected to the planetary gear carrier 5.

Claims (11)

Claims: a5 1. Epicyclic gear with overload protection, in which a lockable gear part by Brake ring parts, which are resiliently supported in both directions of rotation, are held so resiliently against rotation is that it depends on its rotation when a certain torque is exceeded is released, characterized in that the brake ring parts (8) are only freely movable and adjustable on all sides are guided on the lockable gear part and a wedge-shaped space at their joints include, in which the roller-shaped head (10) of a spring-loaded pivotable and axially displaceable lever (12) by springs (53) or hydraulic cylinders (17) is brought to the plant, so that with increasing torque and increasing rotation the brake rings are released. 2. Transmission according to claim 1, characterized in that the application of the brake ring parts (8) by means of longitudinally elastic bands (18) which are under adjustable spring pressure at one end Type takes place that loop around the brake ring parts (8) one or more times (FIG. 4). 3. Transmission according to claims 1 to 2, characterized in that one with levers (12) manually operated switching device (23, 24, 25) is connected, through which the brake ring parts (8) are released can be (Fig. 7). 4. Transmission according to claims 1 to 3, characterized in that the brake ring parts (8) a temperature sensor (27) is provided, which switches off the drive motor Reaching a certain temperature generated by the slip heat (Fig. 12J. 5. Transmission according to claims 1 to 4, characterized in that the pressure of the pressure medium in the cylinders (33) at the ends of the brake ring parts (8) depending on the pivoting the lever (12) is controlled (39, 40; Fig. 13). 6. Transmission according to claims 1 to 5, characterized in that the pumps (31, Fig. 13; 44, Fig. 14) to act on the hydraulic cylinder (17) from the drive shaft (1) driven off. 7. Transmission according to claims 1 to 6, characterized in that the wedge-shaped Space enclosing ends of the brake ring parts (8) have differently steeply inclined surfaces (Figures 8, 9, 10). 8. Transmission according to claims 1 to 7, characterized in that the brake ring device (8, 46 to 51, 57; Fig. 15) is designed as an independent unit and can be attached by means of toothed couplings. 9. Transmission according to claims 1 to 8, characterized in that the lever (12) as Leaf or torsion bar springs are executed (F i g. 18,19, 20). 10. Transmission according to claims 1 to 9, characterized in that the rotation of the Brake ring parts (8) are used to control other brakes. 11. Transmission according to claims 1 to 10, characterized in that a plurality of brake ring devices are provided side by side. Considered publications: German Patent Nos. 397 980, 403 235, 677, 678 478, 700 779, 722 317, 763 529, 785,950 709;
British Patent No. 583 839. For this purpose 2 sheets of drawings 509 628/21 + 7.65 © Bundesdruckerei Berlin