DE1952545A1 - Spur gear with means to eliminate the backlash - Google Patents

Abstract

1320735 Toothed gearing RHEINMETALL GmbH 15 Oct 1970 [18 Oct 1969] 49059/70 Heading F2Q An antibacklash toothed gear drive (e.g. for tank turrets; turnable gun mounts &c.) comprises an output gear 54 driven via two parallel gear trains 38, 40, 43, 47 and 39, 41, 49, 53 from an axially biased (e.g. by a spring 34 or fluid pressure) input shaft 32 integral with two helically toothed pinions 32a, 32b of the same pitch circle and tooth pitch, but with their helix angles of opposite hand, each pinion driving one of the trains. The output gear 54 may have internal teeth. If the shaft 32 is biased by fluid pressure, this may be varied with the input torque. The input shaft 32 may be driven by a gear train 30a, 31, of which one gear 31 is moved normal to Fig. 4 to reduce backlash in this train.

Description

Düsseldorf, the l6. October 1969 Al / J.

File 486

Spur gears with means to eliminate the

Dental planar tip s>

The invention relates to a spur gear with Means for eliminating backlash, in particular straightening gears for armored towers, slewing ring mounts or Like. Of weapon systems.

The correct functioning of straightening systems (height and / or f Side), especially with stabilization devices, depends largely on the backlash-free transmission of the Rotary movement from the drive motor via the straightening gear to the tower or the carriage. .

There are known gears in which a rack means a spring is pressed into a pinion, whereby freedom from play is achieved, but a rotary movement or longitudinal movement only for a limited range of rotation or limited longitudinal stroke at the lowest speeds he follows.

Gearboxes are also known in which a radially split The worm meshes with a mating gear, one half of the worm being firmly connected to a shaft is, while the other half is arranged axially displaceable on this shaft and lockable by nuts is. Also known are drives with power split, in which a pinion of the drive shaft with a Spur gear of the output shaft and at the same time one on the iS ^ drive shaft axially displaceable, helical and second pinion, which can be locked by nuts, meshes with a correspondingly helical spur gear rigidly connected to the output shaft. By moving the

If the pinion is loose, the shafts will twist against each other reached until the backlash of the gears arranged on them is established. With these transmissions However, the freedom from backlash after the setting is also dependent on the degree of wear of the tooth flanks it is only reached with one gear stage within the gear.

In the case of straightening gears, correct operation largely depends on the backlash-free transmission of the rotary motion from the drive motor via the straightening gear to the Turin or take off the mount. With the gears used up to now, special requirements are placed on the surface quality of the tooth flanks as well as compliance with the smallest tolerances in gear manufacturing are required in order to achieve the To reduce the backlash of the individual gear stages to a minimum. The greatest backlash occurs but inevitably due to the summation of the individual backlashes within the gearbox between the output gear and the counter gear, which is usually designed as a toothed arch or ring, on, i.e. outside of the actual straightening gear. Together with radial run-out errors in the toothing of tooth arches or crowns and assembly errors, the backlash can up to several tenths of a millimeter.

The disadvantages outlined above with regard to the backlash are avoided in the known directional gears, for example, that the gear oscillating attached and its output gear by means of compression springs in the The ring gear is pressed in. Here, however, the teeth of one wheel are inserted into the tooth gaps of the mating wheel pressed that a high frictional force, heavy wear on the teeth between the gear output and tower or. Carriage drive and a sluggishness of the gearbox, which is particularly evident at low speed, E.g. when straightening, makes this disadvantageously noticeable through jerky movements.

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The invention is based on the task of gearboxes, in particular straightening gears of the type mentioned at the beginning .zu.treffen measures to eliminate backlash, which, on the one hand, is a constant even with an increase in the tolerances on the output pinion of the gearbox Ensure backlash-free drive in both directions of rotation and freedom of backlash in the reversing point when changing the direction of rotation, on the other hand, it also runs smoothly, combined with the ease of movement of the gearbox itself at the lowest speeds and a reduction in the tooth

ensure flank wear as well as a production engineering and cost ä moderately effective solution.

This object is achieved according to the invention by a below the action of a pressure medium axially displaceable, with helical gears in opposite spiral directions provided with double scratches, the pinion of which is directly or with the interposition of further, independently stored gear stages with the same gear ratio and with correspondingly toothed, coaxial and also independently mounted counter gears are in engagement, each of the mating gears is connected to a further gear by a shaft and The latter gears are of the same size and are arranged directly next to one another and are used as output gears jointly engage in a mating gear located outside the gearbox.

A gear designed in this way is available for the axial when using a suitable pressure medium Moving the double pinion shaft with constant freedom of play with the gear wheel or ring to be driven in Intervention and guarantees smooth, low-noise and low-friction operation even under extreme operating conditions. ,

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In order to keep a straightening gear of the type according to the invention as small as possible in its external dimensions due to the limited space in weapon systems, according to a further feature of the invention, one of the two coaxial mating gears is attached to a solid shaft and the other to a hollow shaft surrounding this solid shaft, wherein the output gears are arranged on the projecting out of the gear housing in each case ¹ ends.

According to the invention, the pressure medium for the axial displaceability of the double pinion shaft is a spring, which on the one hand screwed to the double pinion shaft and on the other hand to one surrounding the spring with the gear housing Threaded bushing is supported.

This spring can be designed, for example, as a helical compression spring or as a disk spring package.

TJm is the calculated torque for such a gear unit to be able to transfer, is in a further embodiment of the In accordance with the invention, the spring force, e.g.> the helical compression spring, adjustable for axial displacement of the double pinion shaft by means of the threaded bushing. A backup against unintentional loosening or adjustment of the threaded bushing can also be provided.

For example, armored towers or slewing ring mounts of weapon systems are often by means of hydraulic or pneumatic Units are driven, the transmission can be driven by a hydraulic in a further embodiment of the invention or pneumatic gear motor, which is connected via a line to a gear unit on the gear unit attached cylinder is connected in which a piston is acted upon by a pressure medium on the cylinder side and rests against the double pinion shaft on the transmission side.

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As a result, when the rotation or Bremsmonientes of the gear drive motor in the cylinder Pressure build-up, which is indirectly applied to both the tooth flanks by means of the piston via the pinion of the double pinion shaft the gear output gears as well as the mating gear acts in such a way that only the currently necessary Tooth flank pressure is achieved and thus the toothing is spared.

According to the invention, the Doppelritze.lv/elle can also § are driven via one or more spur gear stages, which in turn are also backlash-free in a manner known per se are trained.

The drive can be carried out by a toothed wheel that runs loosely on a shaft, which is set in rotary motion on the drive side by means of a spur gear and transfers this rotary motion to another spur gear, which is firmly connected to the double pinion shaft and the connecting line between the three axis centers results in a triangle . The backlash-free of this, the double pinion shaft upstream drive stage takes place i

in that the shaft of the loosely revolving wheel is floating and by one or more screws towards the drive axis and towards the axis of the double pinion shaft can be delivered and is designed to be lockable with play-free contact of the tooth flanks in this position.

Several embodiments of the invention are shown in FIGS Drawings shown and are described in more detail below.

Show it;

Fig. I a two-stage gear designed according to the invention in longitudinal section}

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FIG. 2 is a partial view of FIG. 1 ₍ in which the double pinion shaft is axially hidden by means of a spring; FIG.

3 shows the backlash-free on a greatly enlarged scale Engagement of the driven gears meshing in a counter gear; .

FIG. K shows the axial displaceability of the double pinion shaft according to FIG. 1, but by means of a hydraulic

- liquid or pneumatic medium;

5 shows a four-stage embodiment as a preferred embodiment Gearbox in a representation similar to Fig.

Fig. 6 is a side view of the embodiment according to

Fig..5 seen in the direction of the arrow with partial Breakthrough in the front wall of the housing.

In Figure 1, the double pinion shaft 2 is mounted in a gear housing 1, which is driven via a serration 2a by means of P of a handwheel or a motor (not shown) and on which two equally sized pinions 2b and 2c with the same helical teeth in opposite spiral directions are fixedly arranged. The double pinion shaft 2 is designed to be displaceable in the axial direction by means of a helical compression spring 3. The spring 3, which does not take part in a rotary movement of the shaft 2, is supported on the one hand by a spring plate h and a ball bearing 5 on a collar of the double pinion shaft and on the other hand on a threaded bushing 6 which can be screwed onto a flange formed on the gear housing. ^v The pinion 2b is a mounted on a solid shaft 7 spur gear 8 is engaged. The shaft 7 is means

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a ball bearing 9 inside the gear housing and by means of a second ball bearing 10 outside the gear housing in a cantilever arm that is firmly connected to this 11 stored. At the end of the shaft 7 protruding from the gear housing there is an output pinion designated gear 12, which is screwed to a flange 13 formed on the shaft 7. The pinion 2e meshes with a spur gear 14, which is attached to a hollow shaft j 15 surrounding the solid shaft 7, which in turn by means of ball bearings 1-6, 17 within of the gear housing is mounted. On the gear exit side At the end of the hollow shaft 15, a gear 18 corresponding to the gear 12 is attached. Both output Zethnräder 12 and 18 mesh with a mating gear 19 that is directly connected to a straightening device.

The mode of operation of the above in the basic structure described gearbox is the following:

In an axial shift of the double pinion shaft 2 by means of the spring 3 (Fig. 2) is on the sprocket 2b and 2c due to the oppositely formed oblique (teeth of the sprocket 2b and 2c and the corresponding spur gears 8 and Ik a respective opposite rotational movement of the solid shaft 7 and the hollow shaft 15, which is transmitted to the output spur gears 12 and 18 until their tooth flanks come into contact with the flanks of the mating gear 19 without play (Fig. 3) the output spur gears 12 and 18, for example due to radial runout errors in the toothing of the mating gear 19 or assembly errors, always make noticeable in an axial displacement of the double pinion shaft 2 in or against the force direction of the spring 3.

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In contrast to FIG. 2, FIG. 4 shows the axial displaceability according to Fig. 1, but by means of a hydraulic or pneumatic medium. ■ "

From a hydraulic or pneumatic pump, not shown a gear motor 21 is driven via a line 20; the reflux of the drive means takes place through a line 22. By means of a directional valve 23 » which is adjustable in a known manner, the direction of rotation of the motor 21 can be reversed. Of the Line 20 branches off a line 24 which has a control valve 25 opens into a cylinder 26 which is closed on one side and is flanged to the gear housing 101 and in which a piston 27 is located, which presses through the pressure medium 28 via a ball bearing 105 onto the double pinion shaft 102 guided in the gear housing 101. These engages with its oppositely helical pinions 102b and 102c in correspondingly toothed mating gears 108 and 114, which correspond to gears 8 and 14 in FIG. 1 and lead to the transmission output, the double pinion shaft 102 form-locking via the serration 102a is connected to the motor 21. The axial stroke of the piston 27 is limited by a collar 101a reaches the cylinder from the gearbox side 26 protrudes.

The mode of operation of the hydraulic or pneumatic Device for the axial displaceability of the shaft is the following:

In the event of an increase in the torque or braking torque on the geared motor 21, a pressure builds up briefly on the motor drive side, which is also transmitted to the piston 27 via the lines 20 and 24 and the control valve 25. This thereby exerts greater pressure on the double bit

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wave 102 from, so that the freedom of play already described above of the gearbox up to the output even with the greatest load fluctuations, e.g. with the direction of rotation reversal occurs. After reaching the load speed, such a pressure is established that the Double pinion shaft 102 only with the one for zero backlash just necessary axial pressure is applied.

In contrast to FIG. 1, FIGS. 5 and 6 show a four-stage Transmission, but with the same principle of operation as there.

A pinion shaft 30 mounted in the gear housing 29 drives with its straight-toothed pinion 30a via a spur gear 31 a spur gear mounted on a double pinion shaft 32 33 at. The double pinion shaft, as in the embodiment according to FIG. 1, is under the influence of a spring 3 ^, whose compressive force is caused by a with the gear housing 29 screwed threaded bushing 35 is adjustable, displaceable in the axial direction. Regarding the mode of action reference is made to the description of FIG. 1 for the spring.

According to FIG. 6, the spur gear 31 is in one with its shaft Guide not shown in more detail radially in the direction of the Pinion 30a and the spur gear 33 by means of an adjusting screw 36 deliverable and after contact with the tooth flanks without play of said wheels, by means of a lock nut 37 in this position can be determined.

From the double pinion shaft 32, the drive takes place via the oppositely toothed pinions 32a and 32b to correspondingly toothed spur gears 38 and 39, which are each firmly connected to a pinion 40 and hi. The gear stages 38, kO and 39, hl formed from the pinions and spur gears are mounted in the gear housing 29 independently of one another. The pinion 32a stands up with one

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■■■ ... ■■ ', ■■■ y. 19525-5

a solid shaft 42 attached spur gear 43 via the gear stage 38, 40 in engagement. The shaft 42 is supported by means of a ball bearing 44 inside the transmission housing and by means of a second ball bearing 45 outside the transmission housing in an extension arm 46 that is firmly connected to the latter. At the protruding from the gear housing end of the shaft 42, a designated as an output pinion wheel 47 is mounted, which
is screwed to a flange 48 formed on the shaft 42. The pinion 32b is in engagement with a spur gear 49 via the gear stage 39, ^ i; this
Wheel 49 is attached to a hollow shaft 50 surrounding solid shaft 42, which in turn is supported by means of ball bearings 51, 52 within the transmission. A gear 53 corresponding to gear 47 is fastened to the end of the hollow shaft 50 on the transmission outlet side. Both output gears 47 and 53 jointly engage in a ring gear 54 which runs on a wire ball bearing 55.

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Claims (6)

QKMEBBaBWETAIt Düsseldorf, the ACOKfober Al / J. File 486 Claims (1.) Spur gear with means for eliminating the backlash, in particular straightening gear for armored turrets, turntable laf-et or the like of weapon systems, characterized by an axially displaceable under the action of a pressure medium, with helical gears in opposite spiral directions provided double pinion shaft (-2; 32) with pinions of the same size (2b, 2c or 32a, 32b), which directly or with the interposition of further, independently stored gear ratios (38, '40 and 39, 41) with the same transmission ratio and with correspondingly toothed, coaxial and also independent mutually supported mating gears (8, 14 or 43, ^ 9) are in engagement, and that each of the mating gears each with a further gear (12, 18 or 47, 53) through a shaft (7, 15 or 42, 50) is connected, the latter gear wheels of the same size and lying directly next to each other are arranged and as output gears together in a "outside of the gearbox" Engage the mating gear (19; 5 ^). ■ « 2. Transmission according to claim 1, characterized in that of the two coaxial mating gears (8, 14 or 43, 49) one (8; 43) on one Solid shaft (7; 42) and the other (14; 49) attached to a hollow shaft (15j 50) surrounding the solid shaft is, and that on the opposite shaft ends of the mating gears (8, 14 and 43, 49) driven gears (12, 18 or 47 »53) are arranged. 109818/0929 ~ ² ~ -42 - 3. Transmission according to claim 1 and 2, characterized in that that the pressure medium for the axial displaceability of the double pinion shaft (2; 32) a spring (3J 3 ^) is on the one hand on the Double pinion shaft (2; '32) and on the other hand on a spring (3; 3 ^) surrounding, with the gear housing screwed threaded bushing (6; 35). H. Transmission according to claim 3? characterized geke η η is characterized in that the spring force for the axial displacement of the double pinion shaft (2; 32) can be adjusted by means of the threaded bushing (6; 35). 5. Transmission according to claim Γ and 2, characterized by a hydraulic or pneumatic gear motor (21) which via a line (20, 24) with a cylinder (26) attached to the gearbox housing is connected, in which a piston (27) on the cylinder side is acted upon by a pressure medium (28) and rests on the gearbox side on the double pinion shaft. 6. Transmission according to claims 1 to 5 »thereby g e k e ~ nnzeich.net. * that the double pinion shaft (2; .32) is driven via one or more gear stages, which in turn are known per se . Way are also designed without play. 1 09 81 8/0929