CN106609835B

CN106609835B - Gear box and driving device using same

Info

Publication number: CN106609835B
Application number: CN201510698200.3A
Authority: CN
Inventors: 石晶新; 塔静宁; 赵四军; 张平满; 赵永军; 毕鲁雁; 李书泽; 刘雄辉
Original assignee: Johnson Electric International AG
Current assignee: Johnson Electric International AG
Priority date: 2015-10-23
Filing date: 2015-10-23
Publication date: 2020-03-17
Anticipated expiration: 2035-10-23
Also published as: CN106609835A

Abstract

The invention relates to a gear box and a driving device using the same. The gear box comprises at least one stage of gear transmission mechanism, wherein the gear transmission mechanism comprises two relatively movable elements, and an elastic ring for buffering axial vibration to improve subjective noise is arranged between the two relatively movable elements. The gearbox may be a planetary gear, each stage of the planetary gear train comprising: sun gear, ring gear, a plurality of planet wheel, revolving rack. The planetary wheels are arranged on the rotating frame, and the rotating frame rotates along with the revolution of the planetary wheels. The elastic ring is installed at one side of the rotating frame and used for buffering axial pressure. The present invention reduces or eliminates certain subjective noises by providing an elastomeric ring to limit the vibration of the turret.

Description

Gear box and driving device using same

[ technical field ] A method for producing a semiconductor device

The present invention relates to a drive device, and more particularly, to a gear box used for the drive device.

[ background of the invention ]

The planetary gear box has large bearing capacity and is widely applied. However, when using a helical sun gear, where the load bearing capacity is high, there will be a high axial force inside the planetary gearbox which will result in a high amplitude of the turret oscillation, creating some undesirable subjective noise.

Therefore, a need exists for an improved solution.

[ summary of the invention ]

It is an object of the present invention to reduce some of the subjective noise of a gearbox.

To this end, a first aspect of the invention provides a gearbox comprising at least one stage of a planetary gear train, the planetary gear train comprising: sun gear, ring gear, a plurality of planet wheel, revolving rack. The sun wheel can rotate after being driven, the inner gear ring is fixed to the gear box shell, the planetary wheels are meshed with the sun wheel and the inner gear ring at the same time and revolve around the sun wheel, and the rotating frame is mounted on the planetary wheels and rotates along with the revolution of the planetary wheels. The gear box further comprises an elastic ring mounted to one side of the rotating frame for buffering axial pressure.

As a development, the rotary frame is provided with an annular groove for mounting the elastic ring.

As a refinement, the gearbox comprises a first planetary gear train and a second planetary gear train, the first planetary gear train being a helical gear, the elastic ring being mounted to a carrier of the first planetary gear train.

As a refinement, the elastic ring is located between the carrier of the first planetary gear set and the planet wheels of the first planetary gear set.

As a refinement, the gearbox comprises a first planetary gear train and a second planetary gear train, the first planetary gear train being a helical gear, the elastic ring being mounted to a turret of the second planetary gear train.

As a refinement, the elastic ring is located on the side of the turret of the second planetary gear train remote from the planet wheels of the second planetary gear train.

As a modification, the gearbox includes a first planetary gear train and a second planetary gear train, the first planetary gear train is a helical gear; the gearbox includes a first elastomeric ring mounted to the carrier of the first planetary gear train and a second elastomeric ring mounted to the carrier of the second planetary gear train.

As a refinement, the first elastic ring is located between the carrier of the first planetary gear train and the planet wheels of the first planetary gear train, and the second elastic ring is located on the side of the carrier of the second planetary gear train remote from the planet wheels of the second planetary gear train.

As a refinement, the output of the gearbox includes an end cap, a bearing mounted to the end cap, and an output supported by the bearing so as to be rotatable about a bearing centre, the output being driven by the turret of the second epicyclic gear train, the resilient ring being located between the bearing and the turret of the second epicyclic gear train or between the end cap and the turret of the second epicyclic gear train.

As a refinement, the inner end of the bearing is provided with an outwardly projecting flange for preventing the bearing from disengaging the end cap in a direction away from the planetary gear train.

As a modification, the center of the rotating frame of the second planetary gear train is provided with a non-circular driving hole, and one end of the output member is inserted into the driving hole.

As an improvement, the output piece is a flange provided with a central hole, and the hole wall of the central hole is provided with teeth.

A second aspect of the invention provides a drive arrangement comprising a motor and a gearbox according to the first aspect of the invention, an input of the gearbox being mounted to an output of the motor for decelerating the output of the motor.

The present invention reduces or eliminates certain subjective noises by providing an elastomeric ring to limit the vibration of the turret.

The invention will be further explained with reference to the drawings and the embodiments.

[ description of the drawings ]

FIG. 1 is a schematic view of a drive arrangement provided in accordance with one embodiment of the present invention;

FIG. 2 is a cross-sectional view of the drive device shown in FIG. 1;

FIG. 3 is a schematic view of the drive of FIG. 1 with the gearbox housing removed;

fig. 4 is a schematic view of the drive of fig. 1 with the gearbox housing and bearings removed.

[ detailed description ] embodiments

Referring to fig. 1, a driving apparatus 20 according to an embodiment of the present invention includes a motor 30 and a gear box 40, an output terminal of the motor 30 is connected to an input terminal of the gear box 40, and an output of the motor 30 is decelerated by the gear box 40 and then outputted.

In this embodiment, the motor 30 and the gear box 40 are coaxially installed, i.e., the axial direction of the motor is the same as the axial direction of the gear box 40. But the present invention is not limited to this case.

The housing of the gear case 40 includes a cylindrical portion 42 and an end cap 44 attached to one open end of the cylindrical portion 42. An output 46 of the gearbox 40 is mounted to the end cover 44. In this embodiment, the output member 46 is a flange having a central aperture with teeth on the wall of the central aperture. Preferably, the cylindrical portion 42 has a plurality of flanges 43 near the motor end for preventing rotation of the cylindrical portion 42.

Referring to fig. 2, the gearbox includes two stages of planetary gear trains, each stage of planetary gear train including a sun gear, an annulus gear, a number of planet gears, and a turret. In particular, the first planetary gear train comprises a sun gear 51, three planet gears 52, an annulus gear 53, a turret 54, wherein the annulus gear 53 is fixed to or formed on the inner wall of the cylindrical portion 42 of the gearbox housing, and the planet gears 52 are simultaneously in mesh with the sun gear 51 and the annulus gear 53. The sun gear 51 is mounted to the output shaft 31 of the motor 30 and rotates with the output shaft 31. After the sun gear 51 rotates, the planet gears 52 revolve around the sun gear 51 under the constraint of the sun gear 51 and the ring gear 53. Because each of the planets 52 is rotatably mounted to the turret 54, the turret 54 rotates with the revolution of the planets 52.

The second planetary gear train comprises a sun gear 61, three planet gears 62, an annulus gear 63, and a turret 64, wherein the annulus gear 63 is fixed to or formed in the inner wall of the cylindrical part 42 of the gearbox housing, and the planet gears 62 are simultaneously in mesh with the sun gear 61 and the annulus gear 63. The sun gear 61 is attached to the carrier 54 of the first planetary gear train, and rotates with the rotation of the carrier 54. After the sun gear 61 rotates, the planet gear 62 revolves around the sun gear 61 under the constraint of the sun gear 61 and the inner gear 63. Because each of the planetary gears 62 is rotatably mounted to the turret 64, the turret 64 rotates with the revolution of the planetary gears 62.

In this embodiment, a washer 57 is mounted between the planet gear 62 and the rotating frame 54. End cap 44 of gearbox 40 mounts a bearing 47 for supporting output member 46 such that output member 46 can rotate relative to the gearbox. The center of the turret 64 is provided with a non-circular drive aperture into which one end of the output member 46 is inserted for coaxial rotation with the turret 64. It will be appreciated that the output member 46 may be integral with the turret 64.

Referring to fig. 2 to 4, the bearing 47 is provided with an outwardly projecting flange 48 at the proximal motor end, the flange 48 bearing against the end cap 44 of the gearbox such that the flange 48 is clamped between the end cap 44 and the turret 64 in the axial direction of the gearbox for preventing the bearing 47 from disengaging from the end cap 44 in a direction away from the planetary gear train.

An elastic ring 66 is mounted to the turret 64 of the second epicyclic gear train and is located on the side of the turret 64 of the second epicyclic gear train remote from the planet wheels 62 of the second epicyclic gear train. Preferably, an elastomeric ring 66 is clamped between the turret 64 and the bearing 47 for damping axial forces to eliminate some subjective noise of the gearbox. Further, one of the planetary gear trains (e.g., the first planetary gear train) is a bevel gear to further improve the bearing capacity of the gearbox. In the case of helical gears, the gearbox interior is more susceptible to axial forces. Therefore, in the case of the helical gear, the use of the elastic ring 66 has a better noise reduction effect.

The bearing 47 and/or the turret 64 may be provided with an annular groove for mounting the resilient ring 66.

Preferably, a further resilient ring 56 is mounted to the carrier 54 of the first planetary gear train and is located between the carrier 54 of the first planetary gear train and a washer 57 for damping axial forces to reduce gearbox noise. The turret 54 may be provided with an annular groove for mounting a resilient ring 56.

In an alternative embodiment, only elastomeric ring 66 may be provided without elastomeric ring 56. In another alternative, only the elastomeric ring 56 may be provided without the elastomeric ring 66.

It will be appreciated that the resilient ring 56 may be provided on one side of the turret 54, i.e. the resilient ring 56 may be located between the turret 54 and the planet 52, or may be provided between the turret 54 and the planet 62. Similarly, the elastic ring 66 may be disposed on one side of the rotating frame 64, i.e., the elastic ring 66 may be disposed between the rotating frame 64 and the bearing 47 or between the rotating frame 64 and the end cover 44, and may also be disposed between the rotating frame 64 and the planet wheels 62. However, it is preferable that the planetary gear box 40 has the

elastic rings

56 and 66 provided on the input side and the output side of the

carrier

54 and 64, respectively, and the

carriers

54 and 56 are located between the

elastic rings

56 and 66, as shown in fig. 4. By providing the elastomeric ring 56 on one or both sides of the

turret

54, 64, the turret is effectively restrained from vibration, particularly axial vibration, thereby improving subjective noise. It is to be understood that an elastic ring may be provided between the outer peripheral surface of the turret and the inner peripheral surface of the ring gear in order to restrict the radial vibration of the

turret

54, 64.

It is understood that the cross-section of the

elastic rings

56, 66 may be circular, oval, etc., and may be made of an elastic material such as rubber.

The drive device is particularly suitable for the automobile field as a lifting drive device of an automobile tail gate.

It should be noted that, for a person skilled in the art, several variations and modifications, such as combinations of different features in various embodiments, may be made without departing from the spirit of the invention, and these are within the scope of the invention.

Claims

1. A gearbox comprising at least one stage of a planetary gear train, the planetary gear train comprising:

the sun gear is driven to rotate;

an inner gear ring encircling the sun gear;

the planetary wheels are simultaneously meshed with the sun wheel and the inner gear ring and revolve around the sun wheel;

the rotating frame is provided with a plurality of planet wheels, and the rotating frame rotates along with the revolution of the planet wheels;

the gearbox is characterized by comprising a first planetary gear train and a second planetary gear train, wherein the first planetary gear train is a bevel gear; the gearbox further comprises a first elastic ring (66); the output of the gearbox further comprising an end cap (44), a bearing (47) mounted to the end cap and an output (46), the output (46) being supported by the bearing (47) so as to be rotatable about a bearing centre, the output (46) being driven by a carrier (64) of the second epicyclic gear train, the first resilient ring (66) being located between the bearing (47) and the carrier (64) of the second epicyclic gear train or between the end cap (44) and the carrier (64) of the second epicyclic gear train; the turret is provided with an annular groove for mounting the first resilient ring (66).

2. A gearbox according to claim 1 in which the first resilient ring (66) is located on the side of the turret (64) of the second epicyclic gear train remote from the planet wheels (62) of the second epicyclic gear train.

3. The gearbox according to claim 1, characterized in that the gearbox further comprises a second resilient ring (56), the second resilient ring (56) being mounted to the carrier (54) of the first planetary gear train.

4. A gearbox according to claim 3 in which the second resilient ring (56) is located between the carrier (54) of the first epicyclic gear and the planet wheels (52) of the first epicyclic gear.

5. Gearbox according to claim 1, characterised in that the end of the bearing (47) close to the planetary gear is provided with an outwardly projecting flange (48) against the end cover for preventing the bearing (47) from coming off the end cover (44) in a direction away from the planetary gear.

6. A gearbox according to claim 1 in which the centre of the carrier (64) of the second epicyclic gear train is provided with a non-circular drive bore into which the output member (46) is inserted at one end.

7. Gearbox according to claim 6, in which the output member (46) is a flange provided with a central hole, the wall of which is provided with teeth.

8. A drive arrangement comprising an electric motor and a gearbox according to any one of claims 1 to 7, an input of the gearbox being mounted to an output of the motor for decelerating the output of the motor.