SK1152016U1 - The two-stage speed reduction unit - Google Patents

Abstract

The two-stage speed reducer includes at least one central flange (16) and two front flanges (6), which are housed in two integrated bearings (18), between which are two gears that are coupled using two internal transformers (8) and two outer transformation members (12) for transforming the circular motion of the toothed wheels into a rotational movement originating from the individual gear stages, wherein the inner transforming members (8) and the outer transforming members (12) are annular flat discs with four grooves that engage between the 90 ° angle, and the inner transformers (8) have four grooves open towards the center of the inner transformer member (8) and the outer transformer members (12) have four grooves open outwardly from the center of the outer transformer member (12).

Description

Technical field

The invention relates to a two-stage speed reducer with integrated bearings for providing a high gear ratio between 10: 1 and 100 000: 1 between the input shaft speed and the output shaft speed.

BACKGROUND OF THE INVENTION

Two terms are commonly used in the art: gearbox and speed reducer. The term gearbox is more general than a speed reducer, as the gearbox may have a 'slow' but also 'fast' ratio. The present solution concerns only gearboxes with a gear ratio "slow", therefore we use the name "speed reducer". The term "bearing reducer" refers to the integration of precision gears and radial-axial bearings into a single unit.

For example, SPINEA integrated bearing reducers are currently known in the art. These are single-stage speed reducers using dual cycloid gears in combination with two cross transformers.

There are also known integrated gear reducers from SUMITOMO DRIVE TECHNOLOGIES of the FINE CYCLO type F2C-T series, which are two-speed gear reducers using a planetary gear in the first gear and a double cycloid gear in the second gear.

The prior art rotary gear reducers with integrated bearings achieve high gear ratios in either one gear or two gears, using a first-stage planetary gear and a second-stage cycloid gear. The disadvantage is that such speed reducers are very expensive to manufacture and expensive.

The essence of the technical solution

The present solution differs from the prior art in that the high gear ratio is always achieved in two gears, which may be of different types (for example, cycloid gears or other gears) and are combined with four disc transformers.

The two-stage speed reducer according to the present invention comprises at least one central flange and two front flanges which are housed in two integrated bearings, between which two gears are interconnected, using two internal transformers and two external transformers to transform the circular motion toothed discs for rotational motion coming from individual gears. The inner transformers and outer transformers are four-groove flat discs having a 90 ° groove, and the inner transformers have four grooves open towards the center of the inner transformer, and the outer transformers have four grooves open outwardly the center of the outer transformer. The two-stage speed reducer according to the present invention can be implemented in two versions: a version where the first gear is a double gear and the second gear is a single gear, or a version where the first gear is a double gear and the second gear is a double gear. The twin gears are two gears arranged parallel to each other, the twin gears of the first gear being driven by the two cranks of the input shaft and the twin gears of the second gear being driven by the two eccentric hub eccentrics.

The first gear consists of a double crankshaft input shaft, where two first-gear sprockets are rotatably mounted on both crankshaft of the input shaft, which by their external toothing engage in two roller rims fitted in two front flanges. In each of the two first-stage toothed discs, two short rollers are rotatably mounted which engage two grooves of the inner transformers. The two remaining grooves of the inner transformer members engage two continuous rollers which are rotatably mounted in an eccentric hub rotatably mounted between the cranks of the input shaft.

The second gear consists of an eccentric hub with at least one eccentric, on which at least one second-stage toothed disk is rotatably mounted, which meshes with its external toothing into a central roller ring embedded in the at least one central flange. Two power pins are located in the second gear disc, respectively, and two short power pins are located in the two second gear discs, respectively, engaging the four grooves of the two outer transformers either directly or through the first set of four sliding bushes. The two outer transformers engage in their remaining four grooves two interconnecting pins either directly or by means of a second set of four sliding bushes. Two connecting pins are wedged into two front flanges rotatably mounted in two integrated bearings located in at least one central flange.

The input torque is applied to the input shaft and the output torque can be taken from either the central flange or the front flange.

The input shaft of the two-stage speed reducer is double-crank, with the eccentricities of these keys 0 ° or 180 ° relative to each other, with an eccentric hub with at least one eccentric in which two continuous rollers are rotatably mounted coaxially with the axis of rotation of the input shaft. the eccentric charge is mono-eccentric or bi-eccentric with an eccentricity position e2 of these eccentric centers of 180 ° relative to one another.

As a result, the main components of the speed reducer are simpler and thus less expensive to manufacture. The advantage of the solution is cost savings and easy achievement of high gear ratios.

The gear ratio i of the two-stage speed reducer measured at the central flange is calculated as the product of the gear ratio of the first stage i 1 with the gear ratio of the second stage i2, ie i = il * i2.

The magnitude of the transmission ratio β depends on the number of teeth of the first-stage toothed disk and the number of rollers of the roller rim. The size of the gear ratio i2 depends on the number of teeth of the second-stage toothed disk and the number of rollers of the central roller rim. The toothing of the first-stage toothed disk and the second-stage toothed disk may be of different types, either cycloid or otherwise, for example, chain sprocket.

BRIEF DESCRIPTION OF THE DRAWINGS

The technical solution is explained in more detail in the attached drawings, where:

1 shows an axial section through a two-stage speed reducer in the plane of the spacing bolts pos.17; FIG.

2 shows a detail of pos. 2 - eccentric hub with accessories;

3 shows a detail of pos. 8 - inner transformer,

4 shows a detail of pos. 12 - an external transformer;

5 shows a detail of pos. 9 - second-stage toothed disc with accessories;

6 shows an axial section through a two-stage speed reducer in the plane of the power pins, pos. 10;

7 shows an axial section through a two-stage speed reducer in the plane of the connecting pins pos. 13;

FIG. 8 shows an axial section through a two-stage speed reducer with a doubled second stage in the plane of the short power pins ροζ. 10A, 10B.

EXAMPLES

The two-stage speed reducer is preferably realized according to Example 1 (Figs. 1 to 7) in the following composition: first gear - double gear and second gear - single gear, or in a special composition according to Example 2 (Figs. 2, 3, 4) 8): first gear double gear and second gear double gear. The twin gears are two gears arranged parallel to each other, the twin gears of the first gear being driven by the two cranks 19 of the input shaft 1 and the twin gears of the second gear being driven by the two eccentrics 20 of the eccentric hub 2.

Calculation of gear ratios:

Examples 1, 2 describe a two-stage 368: 1 speed reducer whose basic parameters are:

- eccentricity e 1 = 1.89 mm, eccentricity e2 = 3 mm;

- number of teeth of toothed wheel z1 = 32, number of rollers of roller ring z2 = 34, which corresponds to gear ratio i 1:

= 16 z2- zl 34-32

- number of teeth of the two-stage toothed disc z3 = 44, number of cylinders of the central roller ring z4 = 46, which corresponds to the gear ratio i2:

= ^z4 = ⁴⁶ = 23 ² z4- z3 46- 44 the resulting gear ratio i = i 1 * i2 = 16 * 23 = 368.

That is, the output shaft speed represented by the central flange will be 368 times lower than the input shaft speed, and at the same time the output shaft torque will be 368 times higher than the input shaft torque.

Example 1

1 to 7 show a two-stage 368: 1 speed reducer, wherein the first gear is a double gear and the second gear is a single gear. The two-stage speed reducer comprises at least one central flange 16 and two end flanges 6, which are housed in two integrated bearings 18 between which there are two gears interconnected using two internal transformers 8 and two external transformers 12 for transformation. a circular movement of the toothed wheels for a rotational movement based on the individual gears. The inner transformers 8 and the outer transformers 12 are circular disk-shaped flat discs with four grooves that form an angle of 90 ° therebetween, and the inner transformers 8 have four grooves open towards the center of the inner transformer 8 and the outer transformers 12 have four grooves open outwardly from the center of the outer transformer member 12. The first gear stage consists of a double crankshaft input shaft I, and on both cranks 19 of the input shaft I are rotatably mounted two first-stage toothed discs 4 which engage with their external teeth into two roller rims 5 In each of the two first-stage toothed discs 4, two short rollers 7 are rotatably mounted, which fit into the two grooves of the inner transformer members 8. The remaining two grooves of the internal transformer members 8, two continuous rollers 3, which are shaft 1, engage. The second gear stage consists of an eccentric hub 2 with one eccentric 20 on which the second-stage toothed disc 9 is rotatably mounted, which engages with its external toothing into the central roller rim 15 In the second stage gear disk 9, two power pins 10 engage in the four grooves of the two outer transformers 12 either directly or through the first set of four sliding bushes 11, and the two outer transformers 12 have in their remainder. two interconnecting pins 13 are mounted in four grooves either directly or by means of a second set of four sliding bushes 14. wherein the two interconnecting pins 13 are wedged into two front flanges rotatably mounted in two integrated bearings 18 located in at least one central diameter The input shaft 1 of the two-stage speed reducer is double-crank, with the eccentricity position of the keys 19 0 ° or 180 ° relative to each other, wherein an eccentric hub 2 with one eccentric 20 is rotatably mounted between the cranks 19. continuous rollers 3.

The first gear has a chain toothing and the second gear has a cycloid toothing. The input torque is applied to the input shaft 1 and the output torque can be taken from either the central flange 16 or the front flange 6.

Example 2

In FIG. 2, 3, 4, 8, there is shown a two-stage 368: 1 speed reducer, wherein the first gear is a twin gear and the second gear is a twin gear.

Although this solution is more complex, it provides less bending stress on the input shaft 1.

The two-stage speed reducer comprises at least one central flange 16 and two end flanges 6, which are housed in two integrated bearings 18 between which there are two gears interconnected using two internal transformers 8 and two external transformers 12 for transforming the rotary motion of the toothed wheels into a rotational movement based on the individual gears. The inner transformers S and the outer transformers 12 are circular disk-shaped flat discs with four grooves that form an angle of 90 ° therebetween, and the inner transformers 8 have four grooves open towards the center of the inner transformer 6 and the outer transformers 12 have four grooves open outwardly from the center of the outer transformer member 12.

This solution differs from the solution of Example 1 in that two second-stage toothed wheels are used: the left second-stage toothed wheel 9A. and a right second stage gear wheel 9B. and two left short power pins 10A and two right short power pins 10B.

The first gear consists of a double crank input shaft 1 and two cranks 19 of the input shaft 1 are rotatably mounted with two first-gear sprockets 4, which by their external teeth engage two roller rims 1 fitted in two end flanges 6. In each of the two first-gear sprockets two short rollers 7 are rotatably mounted to engage the two grooves of the internal transformer members 8. The two remaining grooves of the internal transformer members 8 fit two continuous rollers 3 which are rotatably mounted in an eccentric hub 2 rotatably mounted between two cranks 19 of the input The second gear stage consists of an eccentric hub 2 with two eccentrics 20 on which the left second gear tooth disc 9A and the right second gear tooth disc 9B are rotatably mounted. which engage with their external teeth in the central roller rim 15 fitted in the at least one central flange 16. In the left second gear disc 9A, two left short power pins 10A are inserted. and in the right second-stage toothed disk 9B, two right short power pins 10B are engaged together in the four grooves of the two outer transformers 12 either directly or through the first set of four sliding bushes H. The two outer transformers 12 have two interconnecting housings in their remaining four grooves. the pins 13 either directly or by means of a second set of four sliding bushes 14. wherein the two coupling pins 12 are engaged in two end flanges 6 rotatably mounted in two integrated bearings 18 located in at least one central flange 16. The input shaft 1 of the two-stage speed reducer is with an eccentricity position e1 of the cranks 19 0 ° or 180 ° relative to each other, wherein an eccentric hub 2 with two eccentrics 20, in which two continuous rollers 2 and two eccentrics 2 are rotatably mounted, is rotatably mounted coaxially with the axis of rotation. 0 have an eccentricity position e2 of 180 ° to each other.

The first gear has a chain toothing and the second gear has a cycloid toothing. The input torque is applied to the input shaft 1 and the output torque can be taken from either the central flange 16 or the front flange 6.

Industrial usability

The two-stage speed reducer according to the present technical solution can be used in construction, mining, processing, automobile, resp. in other industries, in virtually all areas of technology where low speeds and high torques are required.

Claims (6)

VVv - / Ρ U Protection claims A two-stage speed reducer, characterized in that it comprises at least one central flange (16) and two front flanges (6), which are mounted in two integrated bearings (18), between which there are two gear stages which are connected using two inner transformers (8) and two outer transformers (12) for transforming the circular motion of the toothed discs into rotational motion originating from individual gears, the inner transformers (8) and the outer transformers (12) being flat discs in the form of an annular ring with four grooves that clamp at 90 ° therebetween, and the inner transformers (8) have four grooves open towards the center of the inner transformer member (8) and the outer transformers (12) have four grooves open outward from the center of the outer transformer member (12). 2. The two-stage speed reducer according to claim 1, wherein the first gear is a twin gear and the second gear is a single gear. 3. The two-stage speed reducer of claim 1 wherein the first gear is a twin gear and the second gear is a twin gear. A two-stage speed reducer according to claims 1 and 2, characterized in that the first gear stage consists of a double crankshaft input shaft (1), wherein two first-stage gear wheels (4) are rotatably mounted on both cranks (19) of the input shaft (1). which, with their external teeth, engage two roller rims (5) embedded in two end flanges (6), with each of the two first-stage toothed discs (4) rotatably receiving two short rollers (7) which fit into the two grooves of the internal transformers (8), and the two remaining grooves of the internal transformers (8) engage two continuous rollers (3) rotatably mounted in an eccentric hub (2) rotatably mounted between two cranks (19) of the input shaft (1), and a second the gear stage consists of an eccentric hub (2) with one eccentric (20) on which the second-gear toothed gear is rotatably mounted a disc (9) which, by its external toothing, engages in a central roller ring (15) embedded in at least one central flange (16), the two-stage toothed disc (9) having two power pins (10) engaging the four grooves of the two outer the transformers (12) either directly or through a first set of four sliding bushes (11), and the two outer transformers (12) have two interconnecting pins (13) either directly or through a second set of four sliding bushes in their remaining four grooves (14), wherein the two connecting pins (13) are engaged in two end flanges (6) rotatably mounted in two integrated bearings (18) located in at least one central flange (16). A two-stage speed reducer according to claims 1 to 3, characterized in that the first gear consists of a double-crankshaft input shaft (1), wherein two first-gear sprockets (4) are rotatably mounted on both cranks (19) of the input shaft (1). their external teeth engage two roller rims (5) embedded in two end flanges (6), with each of the two first-stage toothed discs (4) rotatably receiving two short rollers (7) which fit into the two grooves of the inner transformer members (5). 8), and in the remaining two grooves of the internal transformers (8) fit two continuous rollers (3) which are rotatably mounted in an eccentric hub (2) rotatably mounted between two cranks (19) of the input shaft (1), and a second gear stage consists of an eccentric hub (2) with two eccentrics (20) on which the left second stage the toothed disc (9A) and the right second-stage toothed disc (9B), which by their external toothing engage a central roller rim (15) embedded in at least one central flange (16), the left second-stage toothed disc (9A) having two left short power pins (10A), and in the right second-stage toothed disk (9B), two right short power pins (10B) are engaged together into the four grooves of the two outer transformers (12) either directly or through a first set of four sliding bushes (11), and the two outer transformers (12) have two interconnecting pins (13) in their remaining four grooves either directly or by means of a second set of four sliding bushes (14), the two interconnecting pins (13) being wedged into two front flanges (6). rotatably mounted in two integrated bearings (18) located in at least one central bearing flange (16). The two-stage speed reducer according to claims 4 and 5, characterized in that the input shaft (1) of the two-stage speed reducer is double-crank, with the eccentricity position of the cranks (19) 0 ° or 180 ° relative to each other. an eccentric hub (2) having at least one eccentric (20) in which two continuous rollers (3) are rotatably mounted, and the eccentric hub (2) is single or eccentric with an eccentricity position e2 of 180 ° relative to one another.