阅读说明：本技术 传动组件 (Transmission assembly ) 是由 英戈·舒尔茨 于 2019-06-10 设计创作，主要内容包括：公开了一种传动组件(1),所述传动组件(1)包括：太阳齿轮(2),包括外轮齿组(34)；行星架(4),其中,所述行星架(4)绕着所述太阳齿轮(2)设置；齿圈(6),包括内轮齿组(38),所述齿圈(6)围绕所述行星架(4)和所述太阳齿轮(2)；以及至少一个双行星齿轮(8),其中,所述至少一个双行星齿轮(8)附接到所述行星架(4),其中,所述双行星齿轮(8)包括第一轮齿组(32)和第二轮齿组(36),其中,所述太阳齿轮(2)的外轮齿组(34)与所述第一轮齿组(32)啮合,并且其中,所述第二轮齿组(36)与所述齿圈(6)的内轮齿组(38)啮合。(A transmission assembly (1) is disclosed, the transmission assembly (1) comprising: a sun gear (2) comprising an outer set of gear teeth (34); a planet carrier (4), wherein the planet carrier (4) is arranged around the sun gear (2); a ring gear (6) comprising an inner set of gear teeth (38), the ring gear (6) surrounding the planet carrier (4) and the sun gear (2); and at least one double planet gear (8), wherein the at least one double planet gear (8) is attached to the planet carrier (4), wherein the double planet gear (8) comprises a first set of wheel teeth (32) and a second set of wheel teeth (36), wherein an outer set of wheel teeth (34) of the sun gear (2) meshes with the first set of wheel teeth (32), and wherein the second set of wheel teeth (36) meshes with an inner set of wheel teeth (38) of the ring gear (6).)

1. A transmission assembly (1) comprising:

a sun gear (2) comprising an outer set of gear teeth (34);

a planet carrier (4), wherein the planet carrier (4) is arranged around the sun gear (2);

a ring gear (6) comprising an inner set of gear teeth (38), the ring gear (6) surrounding the planet carrier (4) and the sun gear (2); and

at least one double planetary gear (8), wherein the at least one double planetary gear (8) is attached to the planet carrier (4),

characterized in that said double planetary gear (8) comprises a first set of wheel teeth (32) and a second set of wheel teeth (36), an outer set of wheel teeth (34) of said sun gear (2) meshing with said first set of wheel teeth (32), said second set of wheel teeth (36) meshing with an inner set of wheel teeth (38) of said ring gear (6).

2. The transmission assembly according to claim 1, wherein the number of teeth of the first set of gear teeth (32) is different from the number of teeth of the second set of gear teeth (36), wherein the number of teeth of the first set of gear teeth (32) is greater than the number of teeth of the second set of gear teeth (36), or wherein the number of teeth of the first set of gear teeth (32) is less than the number of teeth of the second set of gear teeth (36).

3. Transmission assembly according to any one of the preceding claims, characterized in that it comprises at least one first bearing assembly (40), said at least one first bearing assembly (40) supporting the sun gear (2) with respect to the planet carrier (4).

4. The transmission assembly according to any one of the preceding claims, characterized in that it comprises at least one second bearing assembly (48), said at least one second bearing assembly (48) supporting said planet carrier (4) with respect to said ring gear (6).

5. The transmission assembly according to claim 3 or 4, characterized in that it comprises a monitoring unit configured to monitor the condition of the first bearing assembly (40) and/or the second bearing assembly (48).

6. Transmission assembly according to any of the preceding claims, characterized in that the transmission assembly comprises at least one further double planetary gear (8), the at least one further double planetary gear (8) comprising a first set of wheel teeth (32) and a second set of wheel teeth (36),

wherein the at least one further double planet gear (8) is attached to the planet carrier (4),

the outer set of gear teeth (34) of the sun gear (2) meshes with the first set of gear teeth (32) of the at least one further double planetary gear (8),

the second set of gear teeth (36) of the at least one further double planetary gear (8) meshes with an inner set of gear teeth (38) of the ring gear (6).

7. The drive assembly of claim 6,

the at least one double planetary gear (8) and the at least one further double planetary gear (8) are distributed uniformly in the circumferential direction.

8. Transmission assembly according to any of the preceding claims,

the planet carrier (4) has a rotationally symmetrical shape,

preferably, the planet carrier (4) has an annular shape, or the planet carrier (4) comprises bridges.

9. A robot, in particular a parallel arm robot, comprising a transmission assembly according to any of the preceding claims.

10. A motor, in particular for a motor vehicle, comprising a transmission assembly according to any one of claims 1 to 8.

Technical Field

The present invention relates to a transmission assembly comprising a sun gear, a planet carrier, a ring gear and at least one double planet gear according to the preamble of patent claim 1.

Background

In a robot or other machine, a planetary gear transmission including a sun gear, a ring gear, and a carrier is generally used to transmit a driving force from a driving shaft to an output shaft. Gears and/or double planetary gears may be used to transmit rotation between the elements. In the planetary transmissions used hitherto, a plurality of gears or a plurality of double planet gears or a combination of these are required for the transmission of force between the sun gear and the planet carrier or between the planet carrier and the ring gear.

The planetary transmission in which a plurality of gears or double planetary gears are provided to transmit force (transmission) or rotation (transmission) between a sun gear and a carrier and between a carrier and a bridge, which has been used so far, is positive transmission. "positive transmission" is understood to mean a transmission in which the direction of rotation of the drive and output is the same if it is embodied as a static transmission. This means that when the planet carrier (at least conceptually the planet carrier) does not rotate, the direction of rotation of the sun gear and the ring gear is the same. In the case of high gear ratios (e.g. i >29), if the output becomes driven (e.g. if the motor now acts as a generator), this may result in the transmission being self-locking in one direction.

Disclosure of Invention

It is therefore an object of the present invention to provide a transmission assembly in which the number of gears and/or double planetary gears required can be reduced and self-locking can be avoided.

This object is achieved by a transmission assembly according to patent claim 1. The transmission assembly includes a sun gear having an outer set of gear teeth, a planet carrier disposed about the sun gear, and a ring gear having an inner set of gear teeth, the ring gear surrounding the planet carrier and the sun gear. The transmission assembly further comprises at least one double planetary gear (double planet), wherein the at least one double planet is attached to the planet carrier.

In order to reduce the number of gears and/or double planet gears required, the present invention proposes, compared to known transmission assemblies for transmitting force, to provide a transmission assembly in which a double planet gear is provided, which has a first set of gear teeth and a second set of gear teeth, wherein the outer set of gear teeth of the sun gear meshes with the first set of gear teeth of the double planet gear, and wherein the second set of gear teeth of the double planet gear meshes with the inner set of gear teeth of the ring gear.

In this way, force transmission from the sun gear to the planet carrier (or the double planet gears attached to the planet carrier) and from the planet carrier to the ring gear can be achieved through a single double planet gear. No other gears or double planet gears are required between them (sun and planet carrier or planet carrier and ring gear).

Due to the direct coupling between the sun gear and the planet carrier and the direct coupling between the planet carrier and the ring gear, the transmission assembly is realized as a negative transmission. This means that the sun gear and the ring gear have opposite directions of rotation, assuming the carrier is fixed. Thus, the fixed gear ratio is negative. Whereby self-locking as described above can be avoided.

The ring gear may serve as a housing and may be stationary. Preferably, the ring gear is one-part. Here, the curved force flow may be achieved via the housing (i.e. via the ring gear), rather than via the planet carrier as is the case in other transmission assemblies comprising a fixed planet carrier or a fixed sun gear. Since the housing provides a greater stiffness than the planet carrier, the entire transmission assembly becomes more stable.

The sun gear may be connected to the drive shaft or input shaft and used as a drive. In this case, the planet carrier serves as an output and is therefore connected to the output shaft.

Alternatively, the planet carrier may be connected to the drive shaft or input shaft and act as the drive. In this case, the sun gear serves as an output and is therefore connected to the output shaft. Preferably, this embodiment can be used in the field of parallel arm robots, also referred to as delta robots. delta robots are based on kinematics, in which a platform of three to six linear axes or articulated arms arranged in parallel is guided, the articulated arms being supported in a fixed base. The platform may be provided with a tool such as for example a clamping element. Such kinematic systems typically include three to four articulated shafts that include a fixed drive, such as a motor. These drives may utilize the transmission assemblies described herein. Three-dimensional motion of the platform in direction YXZ is achieved via coordinated actuation of all motors, wherein the platform may also be tilted.

Alternatively, the planet carrier may be fixed and the output/drive may be via the sun and ring gears. This embodiment may be used for driving a vehicle, for example. Here, preferably, the planet carrier is fixedly connected to the vehicle and the ring gear is driven by the motor. In this case, the ring gear serves as an output to the rim or wheel.

According to one embodiment, the number of teeth of the first set of gear teeth is different from the number of teeth of the second set of gear teeth. Here, the number of teeth of the first gear tooth set may be greater than the number of teeth of the second gear tooth set, or the number of teeth of the first gear tooth set may be less than the number of teeth of the second gear tooth set. Due to the difference of the tooth number, the conversion of the driving rotating speed to the output rotating speed can be realized.

Bearings may be used to stabilize the various components, for example, the bearings supporting the planet carrier. Thus, the transmission assembly may comprise at least one first bearing assembly supporting the sun gear relative to the planet carrier. Additionally, the transmission assembly may include at least one second bearing assembly that supports the planet carrier relative to the ring gear.

The first and second bearing assemblies may be tapered roller bearings, ball bearings and/or plain bearings.

In some known drive assemblies, the bearing assembly is exposed to only low rotational speeds, e.g., the bearing assembly is connected only to the slowly rotating output (shaft). Since these bearing assemblies do not perform full revolutions (complete rotations) or rotate too slowly, this may result in insufficient lubrication conditions, and thus lubricant is not sufficiently distributed in the bearing assemblies. This may in turn lead to damage of the bearing assembly and thus premature failure (/ failure) of the bearing assembly.

Since all the bearing assemblies are connected to the planet carrier, if the planet carrier is used as a driver, the bearing assemblies can rotate as the planet carrier rotates. In this way, the bearing assembly (in particular the bearing assembly connected to the ring gear) can rotate at a high rotational speed and a high number of revolutions, i.e. at a rotational speed which drives the planet carrier. In addition, the bearing assembly is rotated 360 ° or more by the planet carrier. Thus, the lubricant is well distributed in the bearing assembly, which prevents the above mentioned disadvantages.

In addition, the bearing assembly may be equipped with a monitoring (/ monitoring) unit for monitoring the condition of the bearing, for example for monitoring the condition of the lubricant. Since the planet carrier is preferably connected to the drive, high rotational speeds (greater than 5 revolutions per second) and full revolutions of the bearing assembly can be ensured. The detection unit may include a sensor located at a fixed position of the bearing inner race or the bearing outer race. If the rotational speed is too low, the sensor generates a noise signal, since such movement does not generate sufficient signal amplitude. However, with the rotational speeds set forth herein, the generated signal is sufficient to determine the condition of the bearing assembly.

According to a further embodiment, the transmission assembly may comprise at least one further double planetary gear comprising a first set of wheel teeth and a second set of wheel teeth. The at least one further double planet gear is attached to the planet carrier, wherein the outer set of teeth of the sun gear meshes with the first set of teeth of the at least one further double planet gear, and wherein the second set of teeth of the at least one further double planet gear meshes with the inner set of teeth of the ring gear.

Since two or more double pinion gears are used, preferably, the two or more double pinion gears are arranged diametrically (diametrically), the arrangement of the sun gear, the arrangement of the carrier, and the arrangement of the ring gear can be stabilized with respect to each other. Due to the second double pinion, radial play between the ring gear, the carrier and the sun gear can be prevented.

In a further embodiment, the transmission assembly may comprise at least one third double planetary gear, particularly preferably the transmission assembly may comprise at least one fourth double planetary gear. These double planet gears each comprise a first set of gear teeth and a second set of gear teeth and are each attached to the planet carrier, wherein the outer set of gear teeth of the sun gear meshes with the first set of gear teeth and wherein the second set of gear teeth meshes with the inner set of gear teeth of the ring gear. With four double planet gears, preferably distributed evenly around the circumference, the forces acting on the planet carrier, the sun gear and the ring gear can be distributed well in the transmission assembly, in particular.

To minimize the clearance between the set of teeth of the first double planet gear and the sun gear or the ring gear, the first set of teeth of the first double planet gear may be further preloaded in the clockwise direction such that the first set of teeth of the first double planet gear contacts the set of teeth of the sun gear. Alternatively, or in addition, the second set of teeth of the first double planetary gear may also be preloaded in the counter-clockwise direction such that the second set of teeth of the first double planetary gear contacts the set of teeth of the ring gear. In this way, the set of teeth of the first double planet gear can be preloaded against the sun gear and the ring gear (tangentially) in two different directions; once in the clockwise direction and once in the counter-clockwise direction. Due to such a preload, contact can be made between the set of teeth of the sun gear or the ring gear and the set of teeth of the double planet gear. In addition, such contact can be maintained even in operation by preloading in different directions and thus avoiding gaps between sets of gear teeth.

If a second double planetary gear is used as described above, the first set of teeth of the second double planetary gear may also be preloaded in the counter-clockwise direction such that the first set of teeth of the second planetary gear set contacts the set of teeth of the sun gear. Furthermore, the second set of gear teeth of the second double planetary gear may be preloaded in the clockwise direction such that the second set of gear teeth of the second double planetary gear contacts the set of gear teeth of the ring gear. The play in the planetary drive can thus also be reduced for the second double planetary gear.

Thus, by using preloaded double planets, play between the sun or ring gear and the double planets can be prevented. Due to the preloading of the second double planet gears, the preloading of the second double planet gears may be opposite to the preloading of the first double planet gears, and thus the backlash between the sets of gear teeth may be better prevented. Furthermore, because of the even force distribution due to the double pinion, the radial clearance between the sun gear, the carrier and the ring gear can be reduced. In particular, the force for preloading of all the gears can be the same here.

If such a transmission assembly is used in a vehicle, in which play between the sun gear or the ring gear and the double planet gears is prevented by using preloaded double planet gears, a very precise drive can be achieved, which makes a high positional accuracy of the entire vehicle possible, in particular in the case of unmanned vehicles or orbital drive systems.

The planet carrier may have a rotationally symmetrical shape. For example, the planet carrier can be configured as a ring. Alternatively, the planet carrier may also comprise a plurality of bridges or discrete arms.

Further advantages and advantageous embodiments are indicated in the description, the drawings and the claims. In particular, the combinations of features specified in the description and the figures are only examples here, so that these features can also be present individually or in other combinations.

Drawings

In the following, the invention will be described in more detail using exemplary embodiments depicted in the drawings. Here, the exemplary embodiments and combinations shown in the exemplary embodiments are only examples, and are not intended to limit the scope of the present invention. The scope of which is limited only by the current claims.

FIG. 1 shows a transmission assembly including a sun gear, a planet carrier, and a ring gear;

FIG. 2 shows a parallel arm robot including the transmission assembly of FIG. 1; and

fig. 3 shows a motor vehicle drive comprising the transmission assembly of fig. 1.

In the following, identical or functionally equivalent elements are denoted by the same reference numerals.

List of reference numerals

1 drive assembly

2 Sun Gear

4 planetary carrier

6 gear ring

8 double planetary gear

10 wheel hub

12 attachment member

14 cover

16 attachment to a driver

18 attachment member

20 cover

22 cover

24 attachment

26 attachment to a preceding part

32 first set of gear teeth

34 outer gear teeth group of sun gear

36 second set of gear teeth

38 inner gear set of gear ring

40 bearing assembly

42 inner ring

44 outer ring

46 rolling element

48 bearing assembly

50 inner ring

52 outer ring

54 rolling element

56 Motor

58 robot arm

60 robot arm

62 platform

64 wheels

Detailed Description

Fig. 1 shows a transmission assembly 1 comprising a sun gear (sun gear)2, a planet carrier 4 and a ring gear (ring gear) 6. Such a transmission assembly 1 may be used as a joint in a robot unit, such as a parallel arm robot (see fig. 2), or as a connection between a motor and a wheel in a motor vehicle (see fig. 3).

Depending on the application, the sun gear 2, the planet carrier 4 or the ring gear 6 may be fixed. In the case depicted in fig. 1, the ring gear 6 is stationary.

One side of the transmission assembly represents the output side and the opposite side represents the drive side. The drive side may be connected to a motor. In the embodiment shown, the sun gear 2 or the planet carrier 4 can optionally be driven via this motor.

If the sun gear 2 is driven, the rotation of the sun gear is transmitted to the carrier 4 via planet gears 8 (planets) provided on the carrier 4, and the planet gears 8 roll on the ring gear 6. On the other hand, if the carrier 4 is driven, the rotation of the carrier is transmitted to the sun gear 2 via the planet gears 8, wherein the planet gears 8 also roll on the ring gear 6.

Hereinafter, the transmission assembly is described in detail with reference to fig. 1.

The carrier 4 is disposed around the sun gear 2. The planet carrier 4 may have an annular shape and be equipped with a plurality of hubs (hubs) 10-1, 10-2 arranged circumferentially around the sun gear 2. The hubs 10-1, 10-2 may be attached to the cover 14 using attachment members 12. The cover 14 may in turn be connected to a driver or output element via an attachment 16.

On the axially opposite side (/ opposite side), the carrier 4 is also connected to the cover 22 using the attachment member 18. Furthermore, the transmission assembly 1 is also provided overall with a cover 20, which cover 20 can be connected to a drive or output element via an attachment 24.

The ring gear 6 can be connected to the housing via the attachment 26, or the ring gear 6 itself can be configured as a housing.

In order to transmit the movement of the planet carrier 4 to the sun gear 2, double planet gears 8-1, 8-2 are provided on the planet carrier. The double planet gears 8-1, 8-2 each comprise a first set of gear teeth 32 which mesh with an outer set of gear teeth 34 of the sun gear 2. The double planet gears 8-1, 8-2 further comprise a second set of internal gear teeth 36 which mesh with a set of internal gear teeth 38 of the ring gear 6. The rotation of the carrier 4 is transmitted or transferred to the sun gear 2 through the first gear tooth group 32. The double planet gears 8-1, 8-2 roll on the ring gear 6 via the second set of gear teeth 36.

As such, the double planet gears 8-1, 8-2 are attached to the planet carrier 4 and directly engage with the sun gear 2 and the ring gear 6. No further additional components, such as gears or planet gears, are provided between the sun gear 2 and the planet carrier 4 and between the planet carrier 4 and the ring gear 6. Due to this configuration of the transmission assembly 1, when it is assumed that the planet carrier 4 is fixed, the sun gear 2 and the ring gear 6 have opposite directions of rotation, and the fixed gear ratio between the sun gear 2 and the ring gear 6 is negative. The transmission assembly 1 is therefore a negative transmission (negative transmission).

The transmission assembly 1 may include a bearing assembly 40 between the sun gear 2 and the planet carrier 4 and a bearing assembly 48 between the planet carrier 4 and the ring gear 6 for supporting the sun gear 2 and the planet carrier 4.

In the embodiment shown, two bearing assemblies 40 are provided between the sun gear 2 and the planet carrier 4. These bearing assemblies each comprise an inner race 42 connected to the sun gear 2 and an outer race 44 connected to the planet carrier 4. Rolling elements 46 (in this case tapered rollers) are disposed between the inner race 42 and the outer race 44. Other types of rolling elements may also be used. Alternatively, the bearing assembly 40 may be a plain bearing.

Furthermore, in the embodiment shown, two bearing assemblies 48 are provided between the planet carrier 4 and the ring gear 6. The bearing assemblies 48 each comprise an outer race 52 and an inner race 50 connected to the planet carrier 4. Outer race 52 may be connected to ring gear 6 or may be formed from ring gear 6, as shown herein. Rolling elements 54 (in this case balls) are provided between the inner race 50 and the outer race 52. Other types of rolling elements may also be used. Alternatively, the bearing assembly 40 may be a plain bearing.

For example, the transmission assembly described in fig. 1 may be used in a parallel arm robot, also known as a delta robot, as shown in fig. 2. In this robot, a platform 62 is suspended via the arms 58, 60. A tool such as, for example, a clamping element, may be attached to the platform 62. Here, platform 62 is connected to a plurality of arms 60-1, 60-2, 60-3 via a joint (e.g., a ball joint), and the plurality of arms 60-1, 60-2, 60-3 are in turn connected to arms 58-1, 58-2, 58-3 via a joint (e.g., a ball joint). The arms 58-1, 58-2, 58-3 are moved by three transmission assemblies 1-1, 1-2, 1-3. Since the arms 58 are arranged obliquely with respect to the respective transmission assembly 1, rotation of the transmission assembly 1 causes a conical movement of the respective arms 58. The movement of the platform 62 can be controlled by these rotations.

The three transmission assemblies 1-1, 1-2, 1-3 are driven by motors 56-1, 56-2, 56-3, respectively. Since the transmission assemblies 1-1, 1-2, 1-3 are similarly constructed, only one transmission assembly 1 will be described below. The motors 56 drive the respective planet carriers 4, the planet carriers 4 transferring their rotation to the sun gear 2 via the planet gears 8. The ring gear 6 is stationary. The sun gear 2 is coupled to and moves the robot arm 58. Since the arm 58 is disposed obliquely with respect to the transmission assembly 1, the rotation of the sun gear 2 is converted into a conical movement of the arm 58.

In another embodiment, the transmission assembly 1 may be used in a motor vehicle, in particular in an electric vehicle, as shown in fig. 3.

In this case, the two wheels 64-1, 64-2 and 64-3, 64-4 are driven via the two motors 56-1, 56-2, respectively. To this end, a transmission assembly 1-1 is disposed between the motor 56-1 and the two wheels 64-1, 64-2, and another transmission assembly 1-2 is disposed between the other motor 56-2 and the two wheels 64-3, 64-4. In this case, the planet carrier 4 is fixedly connected to the vehicle, compared to fig. 2, and drives the sun gear 2 via the motor 56. The ring gear 6 drives the wheels 64.

In summary, in the transmission assembly proposed here, the force transmission (/ gearing) from the sun gear to the planet carrier and from the planet carrier to the ring gear is realized by a single double pinion or by double pinions distributed over the circumference. In this way, it is further possible to avoid the provision of additional gears or double planetary gears between them, whereby the total number of components can be reduced. Furthermore, the transmission can be realized as a negative transmission by a direct coupling between the sun gear and the planet carrier. Since the drive assembly can run backwards and forwards, self-locking (locking) as may occur in a positive drive can be avoided.