WO2001011269A1

WO2001011269A1 - Cycloidal gear pair

Info

Publication number: WO2001011269A1
Application number: PCT/DE2000/002674
Authority: WO
Inventors: Rosmarie Braren; Rudolf Braren
Original assignee: Rosmarie Braren
Priority date: 1999-08-07
Filing date: 2000-08-07
Publication date: 2001-02-15
Also published as: AU6983400A; DE19937412A1

Abstract

A cycloidal gear pair comprising at least a wheel including teeth in the form of an epicycloidal cam (11) matching by form-closure with a wheel consisting of a ball-bearing elements (12) whereof the number is equal to that of the epicycloidal teeth plus 1, and/or at least a wheel comprising teeth in the form of a hypocycloidal cam matching by form-closure with a wheel consisting of a ball bearing element whereof the number is equal to that of the hypocycloidal teeth minus 1. The invention aims at avoiding the occurrence of rotational play in such a gear pair and at easily obtaining a silent functioning. To achieve this, one of the wheels of the pair(s) of wheels, in the zone of meshing, is made from a material with low elasticity, and the other is made from a material with relatively high elasticity.

Description

Z Y K L O I D E N G E T R I E B E

The invention relates to a cycloid gear, which has at least one wheel with an epicycloidal cam as toothing, which mates with a wheel made of rolling elements, the number of rolling elements of which is one more than the number of epicycloidal teeth, and / or at least one wheel with one Hypo-cycloid cam as a toothing, which mates positively with a wheel made of rolling elements, the number of rolling elements is one less than the number of hypo-cycloid teeth.

As an example of such a transmission, reference is made to DE 32 06 992; express reference is made to the explanations there.

When paired with gear wheels, a "V e r d e h s p i e I" is inevitable, even with low quality. The term "backlash" when turning gears and pairs of gears is standardized according to DIN 3960 Sheet 1, Number 5.2.2.1 and means the distance by which a wheel can turn while the counter wheel is held. The size of this game is not standardized, but it increases in practice for a particular gear from zero quality with increasing quality. With changing or reversing power flow or with impacts, this game increases proportionally in strength and generates vibrations and unwanted sound, especially at higher speeds.

The above disadvantages can be reduced by complex oversizing without eliminating the backlash.

However, if the elimination of the torsional backlash is required for an application, such as in robot gears, it is necessary to eliminate this torsional backlash by means of complex measures. In certain other applications it has not been possible to eliminate the disadvantages from the backlash; for example when eliminating the unbearable noise of the turboprop gearbox.

The object of the invention is to eliminate the disadvantages described above and to create low-noise and / or low-play gears with less effort.

This object is achieved in that of the two wheels of the or at least one of the wheel pairs, one in the engagement area consists of a material of low elasticity and the other of a material, in contrast, high elasticity.

In the most general solution of this type, the materials of different elasticity only play a role insofar as they have to meet the requirements given here with regard to their strength, machinability or the like. In a preferred embodiment, the transmission parts in the engagement area are formed on the one hand from a metallic material and on the other hand from a non-metallic material with an elastomeric property, in particular a plastic in the form of an artificial or natural elastomer. The rolling element ring can particularly preferably be formed by commercially available camshaft toothed belts with a partially circular shape in cross section, the teeth of the toothed belts corresponding to the equidistant parameter and the circular toothed belt corresponding to the parameter r of the basic and rolling circles of the corresponding cycloids.

In a further particularly preferred embodiment, the wheel with the more elastic material, viewed in the direction of the other stiffer wheel, is larger than the teeth of the other; This eliminates the game even with changing or reversing friction and in both directions. Such training can also compensate for manufacturing tolerances. This embodiment therefore allows the tooth engagement to be designed in such a way that even when there is no torque load due to compression of the gear wheel made of the more elastic material, there is no free play.

The invention is explained in more detail below with reference to drawings. Show it: Figure 1 is a longitudinal section in a schematic representation of a cycloidal gear with an EPI cycloid and with a clutch, the task of which is to produce the required speed and torque conversion between their three connecting shafts in the central axis. (The elastic material is assigned to either the cam disc or the rolling elements.

1.1 shows a partial cross section, limited to the cam disk and rolling elements, along the line I-1 in FIG. 1;

Figure 2 is an axial longitudinal section in a schematic representation after a cycloidal gear with a double cam, and an additional ring gear instead of the clutch. the elastic material becomes either the double; Cam or the rolling elements and assigned. 2.1 shows a partial cross section along lines II-II in FIG. 2; 2.2 shows a partial cross section along the lines III-III in FIG. 2; Fig. 3 shows a longitudinal section in an exemplary embodiment for an outer planet rear axle in commercial vehicles with an EPI cycloid and with a HYPO cycloid; (The elastic material is preferably assigned to the rollers 312.3.)

Fig. 3.1 a cross section along the lines l-l in Fig. 3.

Fig. 4 shows an axial longitudinal section through a cycloidal gear with three parallel-acting cams with a balanced eccentric arrangement.

As can be seen from Figures 1 and 1.1, the connecting shaft 1 - analogous to all closed gears - represents one of the three "connecting shafts" and forms a non-rotatable unit together with a web designed as an eccentric 4 with a roller bearing seat 5 and moves via an eccentric bearing 7 Cam 10. The cam 10 with its parameter r and with its curve 11 pairs in a ring in the housing 2 with the rolling elements 12 and is centered and fastened to the bearing part 13 via a clamping sleeve 14. Another "connecting shaft" is the housing 2 together with the non-rotatably connected bearing part 13, the bearings of which take place on the central axis on the one hand via the roller bearing 8 and on the other hand via the roller bearing 9.

The third "connecting shaft" 3 formed with the bearing seat 6 is with a

Coupling 15 rotatably connected, the flow of forces via a screw 16 with the

Cam 10 takes place. The elastic material is assigned to a part of the pairing, namely either the cam plate 10 in one embodiment - cross-hatched as partial area 11 'on the right in FIG. 1.1. indicated - or the rolling element 12 in the other embodiment - cross-hatched as a portion 12 ^* left in Figure 1.1. indicated -. Commercially available camshaft timing belts are advantageous to use here instead of the rolling elements 12.

2 and 2.1 and 2.2 follow analogous designations like FIG. 1 with the following changes:

Instead of the cam plate 10, the double cam plate 110 acts when the

Clutch 15; the pairings of the double cam plate 110 once with the larger rolling element ring

112.1 - Figure 2.1 - the connecting shaft 102 and the other with the smaller one

Rolling ring 112.2 - Figure 2.2 - the connecting shaft 103 results depending on the choice of

Curved teeth the ratio from 20 to 2,000.

The connecting shaft 101 rotatably receives the bearing seats 105 and 106 and the eccentric 104 serving as the bearing seat, so that the connecting shaft 103 receives the central bearing via the crossed roller bearing 109.1 and the bearings 108 and 109. With 107 the eccentric ball bearing is designated, with 113 and 114 a bearing seat for the crossed roller bearing 109.1 opposite the connecting shaft 102, the other bearing seat is provided on a correspondingly projecting design of the connecting shaft 103, which also cooperates with the smaller Welzkörperring.

The elastic material is used as described in Fig. 1.

As an example of such a transmission type, reference is made to DE 19645825 A1.

3 and 3.1 show the use of EPI and HYPO cycloids in an embodiment for outer planet rear axles in commercial vehicles. The use of elastic material in the form of commercially available parts for the rollers 312.3 is particularly favorable here.

The longitudinal section shown in FIG. 4 of a cycloidal gear in accordance with one according to DE 3206992, in which the rolling elements 412.1; 412.2; 412.3 the cam disks 410.1; 410.2; 410.3; the eccentric bearings 407.1; 407.2; 407.3; the eccentrics 404.1; 404.2; 404.3; are divided 3-fold according to the list so that the two outer parts are dynamically equivalent to the individual inner part and secondly that the two outer parts are offset by 180 ° from the individual inner part, with the same eccentricity of all parts. The two outer rolling element rings are replaced by commercially available toothed belts.

For the rest, the details of the above-described exemplary embodiments, together with modification and adaptation variants, are recorded in the attached “parts list”. The above-described gearbox examples can accordingly have EPI or HYPO cycloids, as indicated in the list, in which, apart from the names of the components, reference numbers are also given below under "Cycloid and rolling element change - the respective changes are specified when changing to the other curve type.

S t ii c k 1 i s t e

Embodiment Λusführungsbei game

S c h e m a S c h e m a Outer planetary axis EPI cycloid gear.

Fig. 1 with clutch Fiq. 2 with double curve Fiq. 3 with EPI and Fiq. 4 3x parallel HYPO cycloids separate parts

1 eccentric connecting shaft 101 eccentric conn. 301 Exzente-An.W. 401 eccentric An.W.

2 housing connection shaft 102 housing connection w. 302 recordings. 402 housing An.W.

3 Coupling connection shaft 103 sheath-on. elle 303 HYPO-Z. Hollow 403 Coupling An.W.

4 eccentrics 104 eccentrics 304 eccentrics 404.1 eccentrics

404.2 eccentric

404.3 eccentric

5 Housing bearing seat 105 Housing bearing seat 305 axle bridge

6 Wrapping bearing seat 106 Wrapping bearing.

7 eccentric bearings 107 eccentric bearings 307 eccentric bearings. 407.1 eccentric bearing

407.2 eccentric bearing

407.3 Eccentric bearing

8 housing bearings 108 housing bearings 308 E-shaft bearings

9 Envelope bearing 109 Envelope bearing 309 Axle bearing 109.1 Cross roller bearing

10 cam 110 double cam. 410.1 Cam

410.2 Cam

Pair variation: 410.3 cam

1. Part 11 with part 12; 11 EPI cycloid train 111.1 EPI cycloid train 311 EPI cycloid - -

2. Part 11 with part 12 "; 11 'elastic EPI cycloid 111.2 EPI cycloid train

3. Part ll'with part 12; 12 whale bodies 112.1 rolling elements 312 rolling elements 412. .1 elast. Wälzkö.

12 'elastic rolling element 112.2 rolling element 312.3 roller 412, .2 rolling element 412..3 elastic. Wälzkö.

13 Envelope 113 bearing part 313 bell hub not designated

14 adapter sleeve 114 adapter sleeve 314 cover

15 clutch

16 screw connection screw Part 303 with 114;

Part 11 with part 15 part 303 with 313

17 circlip not designated

W e c h s e l of EPI cycloids in rolling elements and of rolling elements in HYPO cycloids with the same operating

conditions

Part 11 in rolling elements Part 111.1 / 111.2 in Wälzkö. Part 303 in Wälzkö. Part 410 in rolling elements Part 12 in HYPO cycloids Part 112.1 / 112.2 in HYPO-Z. Part 312 in EPI u. Part 412 in HYPO cycloid

HYPO-Z.

Part 311 in Wälzkö.

Claims

claims

1. Cycloidal gear, which has at least one wheel with an epi-cycloid cam as toothing, which mates positively with a wheel made of rolling elements, the number of rolling elements of which is one more than the number of epi-cycloid teeth, and / or at least one wheel with a hypo- Has cycloidal cam as a toothing, which mates positively with a wheel made of rolling elements, the number of rolling elements of which is one less than the number of hypo-cycloid teeth, characterized in that one of the two wheels or at least one of the wheel pairs has less of one in the engagement area made of one material Elasticity and the other consists of a material in contrast high elasticity.

2. Cycloidal gear according to claim 1, characterized in that the one wheel of the at least one wheel pair is formed at least in its engagement area from a metallic material and the other wheel at least in its engagement area from a non-metallic material with an elastomeric property.

3. Cycloidal gear according to claim 2, characterized in that the wheel of the at least one pair of wheels made of a metallic material, in particular high-strength steel, and the other wheel made of a plastic - in particular natural or artificial elastomer.

4. Cycloidal transmission according to one of claims 1 to 3, characterized in that the rolling element ring is formed by commercially available and circular camshaft toothed belts, the teeth of the toothed belt being the equidistant parameter and the circular toothed belt being the parameter (r) of the basic and rolling circles correspond to the corresponding cycloid.

5. Cycloidal transmission according to one of claims 1 to 4, characterized in that the wheel with elastic material is made larger than the toothing of the other when viewed in the direction of the other wheel, in order to eliminate the play in the event of changing or reversing adhesion or in the event of impacts.