DE1550730C - Spur gear planetary gear with load compensation - Google Patents

Description

men will be. Due to the resulting short overall length of the gearbox, which is not only desirable but also essential for many applications, there is also a reduction in manufacturing and acquisition costs.

Advantageous refinements of the invention are specified in the subclaims. It is in itself known (USA.-Patent 1 345 089), a bending rod at one end to enable To provide compensatory movements with a ball joint.

The invention is illustrated in the drawing using several exemplary embodiments. It shows

F i g. 1 shows an axial partial section through a spur planetary gear with single helical teeth,

F i g. 2 shows a partial section of the same type, with parts omitted, which are essential for an understanding of the invention are not essential

F i g. 3 the partial axial section through the fastening of the flexible rod in the planet carrier,

F i g. 4 a further partial axial section through a

Axial bearings for two directions of force and finally F i g. 5 is an axial partial section in which the

Flexible rod with a ball head or the like

In Fig. 1, the bending rod 1 is arranged with its end 1 α in the divided cover 2, which in turn is firmly connected to the planet carrier 3. On the face of the cover 2 facing away from the planet carrier 3 there is also the auxiliary sliding surface 2a . The bending rod 1 is passed through the hollow inner central wheel 4 and is provided with a forged or attached washer Ib which accommodates the sliding bearing 5 or is part of it. The inner central wheel 4 is supported constitute with its flange-like end 4 of a disc to Ib of the bending rod 1 from. The oil is supplied and from the outside in the direction of the arrow through the gearbox then passes through the bore Ic provided in the bending rod 1 to the sliding bearing 5. It has been found to be useful that the length of the bending rod 1 is a multiple, preferably ten to fifteen times, its Diameter d is.

In Fi g. 2 is basically the same gear as in F i g. 1 and provided with the reference numerals used there; the hole rf in the bending bar is omitted. · Here it is the behavior of the bending rod 1 with its sliding bearing as well as that of the inner one Central wheel 4 shown. When the inner central wheel 4 is inclined, it is caused, for example Due to toothing errors, if the axial plain bearing 5 is rigidly fastened, the plane surfaces would tilt respectively. A tilting od. The like. However, due to the elastic or resilient arrangement of the Bending rod 1 avoided because it aligns with the inner central wheel 4. The central wheel is in labeled 6 in both figures.

Also in Figs. 3, 4 and 5 are the individual parts, so far they with those of the F i g. 1 and 2 coincide with the same reference numerals.

In Fig. 3 it can be seen that the bending rod 1 without support by the cover 2 directly on or in the Planet carrier 3 is attached.

According to FIG. 4, the thrust bearing 5 by expanding in the inner central wheel 4 that this over the flange 1b of the flexure bar 1 away accesses and a disc 7 receives the second, forms with 5 α called bearing point, is produced whereby a thrust bearing for two opposite directions of force. The disk 7 is secured in the axial direction by the spring ring or the like 8. The oil passes through the bending bar in the same way as in FIG. 1; of the hole 1 c of the oil passes through the transverse bore Id to the plain bearing points 5 and 5a, respectively.

According to FIG. 5, the bending rod 1 is also fastened directly to or in the planet carrier 3 without support by the divided cover 2. The end of the bending rod 1 opposite the planet carrier 3 and passed through the inner central wheel 4 is provided with a ball 9 or with a ball section. The ball is encompassed by the disk 10, 10 α divided in the radial direction at 10 b like a dome. The fixed in the ball 9 pin 11 engages with play in the groove 10 c of the two-part bearing plate 10, 10 a a. A plurality of circumferentially arranged distributed studs 12 keep the two plate halves 10,10 together α.

1 sheet of drawings

Claims (5)

1 2 patent claims arranged fixed to the housing and the inner gear is mounted on one side in the housing. Storage takes place there- 1. Single helical-toothed spur gear-planetary in the axial and radial direction by means of slide bearings, gearbox, with a hollow design, penetrated by a flexible rod with herringbone gears, although such a gearbox has certain advantages compared to gearboxes, it is / has internal central gear, that with which the rotation also suffers from certain shortcomings. For the optimoment incoming or outgoing part articulately correct power distribution to the individual power groups and with means for receiving axial strands as well as to the tooth widths, the forces are provided in at least one direction, free adjustability of the inner central gear is characterized by this that the beer is long. The degree of freedom can not be achieved by large rod (1) with its one end (1 a) on the long-precision in the manufacture of the toothing, the rotating gear side on the stationary planetary bearing and the bearing point for the inner or rotating gear member, preferably pia- Central gear to be replaced. In addition, the inner carrier (3), firmly clamped and at its inner central wheel, should be able to carry out compensatory movements in all levels, through the inner central wheel (4), on the one hand from the tooth and guided end to accommodate axial sliding bearing errors and on the other from the flexibility of the gers (5) is expanded like a flange on which the ring gear depend. It is therefore obvious that an inner central wheel (4) designed in the same way supports this freedom for the compensatory movements. proposed inner central gear is not given. 2. Planetary gear according to claim 1, characterized 20 In addition, the overall length is due to the storage and characterized in that the attachment of the bending rod is achieved by the specially attached tooth coupling hub bes (1) on the planet carrier (3) by a divided considerably enlarged. th cover (2), which is attached to its tarpaulin. t carrier (3) facing away from the end with an auxiliary toothed spur planetary gear tried that sliding surface (2 d) is provided. 25 axial forces of the unsupported, freely adjustable inner 3. Planetary gear according to claim 1 with a ren central wheel on thrust rings to accommodate thrust bearings for two directions of force, thereby ge (German Auslegeschrift 1 165 370). In this case, that the inner central (4) away but engages over a free adjustability of the inner central Raden flange (1 b) of the bending rod (1) is jekennzeichnet, does not ensure the. Due to the abutment of the flanks and a washer (7), which the second 30 of the pressure rings on each other, a shift of the bearing point (5 a) is formed. Gear axles from their parallel position and 4. Planetary gear according to claim 1, thereby possible. characterized that the bending rod (1) at its end with a ball (9) or with a Ku-35 (Swiss patent 253 321) is a power-splitting gear according to the starting point of the invention, which is guided through the inner central wheel (4) ), in which the gel section is provided, which is hollow from the radially inner central wheel and is encompassed by a split-direction bearing disk (10, 10 a) kalot- an extension of the drive shaft forming bidding (10 b) , the ball (9) is carried rod. This flexural rod, the length or the spherical section with a pin (11) naturally looks a multiple of its diameter, which makes with play in a groove (10 c) of 40, allows a transverse deviation of the inner bearing washer (10 , 10 a ) intervenes. Central wheel. For the transmission of the drive torque 5. Planetary gear according to one of the preceding is one of the bending rod comprehensive Doppelkupphenden claims, characterized in that treatment is provided that the evasion of the bending rod of the bending rod (1) for lubrication reasons is formed hollow axis of rotation in the transverse direction to achieve a and its length is ten - Permitted up to 45 even load.
Fifteen times its diameter (d) . The disadvantage of the known transmission is in the Construction costs for the means to transfer the property seen driving moment. The drive shaft must _; exactly with that. Bjegestab. be centered to avoid unbalance In order to ensure even load distribution over the full 5 ° appearances, the "with the rotating bending rod too Achieving len face widths require planetary damage or breakage, safely too Drives with herringbone gearing avoid a relatively large con-figure. structural effort (prospectus »Maag -planet- The invention is based on the task of a drives «). This effort can be increased, for example, in single helical epicyclic gears the separation of the central gears and their cardani- 55 create an even load distribution shear suspension in double tooth clutches, in which on the individual .L. power lines as well as over the elastic arrangement of the ring gears by means of spring-tooth width with good efficiency and lower of the elements and other more noticeable · The construction length is made possible. The result of such an effort are technically jsqmpli- The inventive solution uses a known one adorned and therefore quite expensive gearbox. To reduce the mounting of a rotating bending rod with 60 (USA change this effort and thus also the manufacturer's patent specification 1 224 882), which is also at his Development and acquisition costs are like spur gear - one end carries a rotating element and its Planetary gear with single helical toothing has a flange for mounting on other guided ends turns. has a thrust bearing, which, however, has rolling elements It is a spur planetary gear with simple 65 contains. Helical gearing has been proposed (Swiss- According to the solution according to the invention, the see patent specification 360 857), in which the outer zen axial thrust is self-adjusting on all sides The non-tilting axial plain bearing is received via a thin-walled connecting link.