SK7867Y1 - The two-stage speed reduction unit - Google Patents

Abstract

The two-stage speed reduction unit comprises at least one central flange (16) and two end flanges (6) stored in the two integrated bearings (18), between which there are two gears. The gears are connected by two inner transformation members (8) and two outer transformation members (12) to transform the circular motion of gear wheels in rotary motion based on the particular gear. The inner transformation members (8) and outer transformation members (12) are flat disks in the shape of a circular ring with four grooves which, forming the 90 ø angle to each other. The inner transformation members (8) have four grooves open towards the center of the inner transformation member (8) and outer transformation members (12) have four grooves opened to the outside from the center of the outer transition member (12).

Description

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 relates exclusively to gearboxes with a gear ratio "slow", therefore the name of the speed reducer is used. The term bearing reducer refers to the integration of precision gears and radial-axial bearings into one unit.

For example, speed reducers with integrated bearings from SPINEA are currently known in the art. These are single-stage speed reducers using a double cycloid gearing in combination with two cross-member transformers.

There are also known integrated speed reducers from SUMITOMO DRIVE TECHNOLOGIES of the LINE CYCLO type L2C-T series, which are two-stage speed reducers using a planetary gear in the first gear and a dual 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 in combination 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 there are two gears interconnected by using two inner trans -ormating members and two outer trans -ormating members to transform the circular motion of toothed discs for rotational motion coming from individual gears. The inner transformers and outer transformers are flat circular disk-shaped discs with four grooves that are 90 ° apart, 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 translating member. 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 in 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 both first crankshaft sprockets are rotatably mounted on both cranks 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 fit into the two grooves of the inner translating members. The two remaining grooves of the inner translating 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 disc is rotatably mounted, which by its external toothing engages in a central roller rim 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 in the four grooves of the two outer translocation members either directly or through the first set of four sliding bushes. The two outer transformers have two connecting pins in their remaining four grooves, either directly or through a second set of four sliding bushes. The two connecting pins are connected to the two front pins

SK 7867 Yl reverse rotatable 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 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 gear i1 with the gear ratio of the second gear i2, hence 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 gear tooth and the second gear tooth may be of different types, either cycloid or other, e.g.

BRIEF DESCRIPTION OF THE DRAWINGS

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

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

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

FIG. 3 shows the detail of pos. 8 - an internal transformer;

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

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

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

FIG. 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 - twin gear and second gear - twin gear. The twin gears are two gears arranged parallel to each other, the twin gears of the first gear being driven by two cranks 19 of the input shaft 1 and the twin gears of the second gear being driven by two eccentric hubs 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 e1 = 1.89 mm, eccentricity e2 = 3 mm;

- the number of teeth of the toothed wheel z1 = 32, the number of rollers of the roller ring z2 = 34, corresponding to the gear ratio il:

III = zl z2- zl

34- 32

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

j = ^z4 = ⁴⁶ = 93 ² z4- z3 46-44

SK 7867 Υ1 resulting gear ratio i = il * 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

In FIG. 1 to FIG. 7 shows a two-speed 368: 1 speed reducer, wherein the first gear is a twin 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 consists of a double-crankshaft input shaft 1 and two cranks 19 of the input shaft 1 are rotatably mounted with two first-stage toothed discs 4, which engage with two external roller teeth 5 Two short rollers 7 are rotatably mounted in each of the two first-stage toothed wheels 4, which fit into the two grooves of the inner transformer members 8. The other two grooves of the internal transformer members 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 meshes with its external toothing into the central roller rim 15, which is inserted. in the at least one central flange 16. In the second gear tooth disk 9, two power pins 10 are received which 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 remaining four. two interconnecting pins 13 either directly or by means of a second set of four sliding bushes 14, wherein the two interconnecting pins 13 are engaged in two end flanges 6 rotatably mounted in two integrated bearings 18 located in at least one central The input shaft 1 of the two-stage speed reducer is a double-crank, with a relative eccentricity position of the keys 190 ° or 180 ° relative to each other, wherein an eccentric hub 2 with one eccentric 20 is rotatably mounted between 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 11 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 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.

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

The first gear consists of a double crank input shaft 11 and two cranks 19 of the input shaft 1 are rotatably mounted with two first-gear sprockets 4, which by their external toothing engage in two roller rims 5 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 shaft L The second gear consists of an eccentric hub 2 with dv4

SK 7867 201 with eccentrics 20, on which the left second stage gear wheel 9A and the right second stage gear wheel 9B are rotatably mounted, which by their external toothing engage in a central roller rim 15 fitted in at least one central flange 16. In the left second stage gear wheel 9A the two left short power pins 10A and in the right second gear tooth disk 9B are fitted two right short power pins 10B jointly engaging the four grooves of the two outer transformers 12 either directly or through the first set of four sliding bushes 11. The two outer transformers 12 have in their the other four grooves mounted two connecting pins 13 either directly or by means of a second set of four sliding bushes 14, the two connecting pins 13 being wedged into two end flanges 6 rotatably mounted in two integrated beds The input shaft 11 of the two-stage speed reducer is double-crank, with a relative eccentricity position of the keys 190 ° or 180 ° relative to each other, wherein an eccentric hub 2 with two eccentrics 20 is rotatably mounted between the cranks 19. in which two continuous rollers 3 are rotatably mounted, and the two eccentrics 20 have an eccentricity position e2 of 180 ° relative to one another.

The first gear has a chain toothing and the second gear has a cycloid toothing. The input torque is applied to the input shaft 11 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.

PROTECTION REQUIREMENTS

Claims (7)

by the first transfer, that the first transfer and by the first pre1. 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 gears connected by two the inner transformers (8) and the two outer transformers (12) for transforming the circular motion of the toothed discs into rotational motion originating from the individual gears, the inner transformers (8) and the outer transformers (12) being annular flat discs with by four grooves that clamp 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 outward from the center of the outer transformer ( 12). The two-stage speed reducer according to claim 1, characterized in that the output stage is a double transmission and the second gear stage is a single transmission. A two-stage speed reducer according to claim 1, characterized in that the output stage is a double transmission and the second gear stage is a double transmission. The two-stage speed reducer according to claims 1 and 2, characterized by a water stage consisting of a double-cranked input shaft (1), wherein two first-stage gear wheels (4) are rotatably mounted on both cranks (19) of the input shaft (1). engage in two roller rims (5) embedded in two end flanges (6), wherein each of the two first-stage toothed discs (4) is rotatably mounted with two short rollers (7) which fit into the two grooves of the inner transformer members (8), and in the remaining two grooves of the internal transformers (8), two continuous rollers (3) are received which are rotatably mounted in an eccentric hub (2) rotatably mounted between two cranks (19) of the input shaft (1), and the second gear comprises from an eccentric hub (2) with one eccentric (20) on which a second-stage toothed disc (9) is rotatably mounted, which its external toothing engages in a central roller rim (15) embedded in at least one central flange (16), wherein two power pins (10) are located in the second-stage toothed disk (9), engaging in four grooves of the two outer transformer members (12) directly or through the 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 through a second set of four sliding bushes (14), two the interconnecting pins (13) are engaged in two front flanges (6) rotatably mounted in two integrated bearings (18) located in at least one central flange (16). The two-stage speed reducer according to claims 1 and 3, 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 by its external toothing za5 SK 7867 Y1 are received in two roller rims (5) embedded in two end flanges (6), wherein each of the two first-stage toothed discs (4) is rotatably mounted with two short rollers (7) which fit into the two grooves of the inner transformers (7). 8), and two continuous rollers (3), which are rotatably mounted in the eccentric hub (2), fit into the remaining two grooves of the inner transformers (8), 5 is rotatably mounted between two cranks (19) of the input shaft (1), and the second gear consists of an eccentric hub (2) with two eccentrics (20) on which the left second stage gear disc (9A) and the right second stage gear discs (9B), which by their external toothing engage a central roller rim (15) embedded in at least one central flange (16), with two left short power pins (10A) mounted in the left second gear disc (9A), and In the second stage gear disc (9B), two right short power pins (10B) are engaged together into 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 (12B). ) have two connecting pins (13) in their remaining four grooves, either directly or by means of a second set of four sliding bushes (14), the two connecting pins (13) being wedged into two front flanges (6) 15 rotatably mounted in two integrated bearings (18) located in at least one central 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. rotary eccentric hub (2) 20 with at least one eccentric (20) in which two continuous rollers (3) are rotatably mounted, and the eccentric hub (2) is mono-eccentric or bi-eccentric with an eccentricity position e2 of 180 ° relative to one another. 7 drawings