CN112010215B

CN112010215B - Speed reducer and winch using same

Info

Publication number: CN112010215B
Application number: CN201910465870.9A
Authority: CN
Inventors: 游文杰
Original assignee: Rexon Industrial Corp Ltd
Current assignee: Rexon Industrial Corp Ltd
Priority date: 2019-05-30
Filing date: 2019-05-30
Publication date: 2022-05-17
Anticipated expiration: 2039-05-30
Also published as: CN112010215A

Abstract

A speed reducer has a differential gear speed reducing mechanism and a planetary speed reducing mechanism. The tooth difference reducing mechanism comprises a first inner gear ring and a transmission gear which are arranged adjacently, a sun gear and a plurality of first planetary gears which are arranged in the first inner gear ring and the transmission gear, and the tooth numbers of a first inner ring tooth part of the first inner gear ring and a second inner ring tooth part of the transmission gear are different. The planetary speed reducing mechanism comprises a second inner gear ring, a planetary support and a plurality of second planetary gears, a first output gear shaft of the transmission gear extends into the planetary speed reducing mechanism and is meshed with the planetary gears, and a second output gear shaft is arranged on one side of the planetary support, which is opposite to the gear difference speed reducing mechanism. Through the structural design of the speed reducer, the number of elements can be effectively reduced, and a sufficient speed reduction effect is achieved.

Description

Speed reducer and winch using same

Technical Field

The invention relates to a winch, in particular to a speed reducer and a winch using the speed reducer.

Background

The traditional winch for pulling heavy objects (for example, vehicles to be rescued) uses a planetary gear reducer as the internal reducer. Although the conventional planetary gear reducer has a heavy load characteristic, the reduction ratio is also low. Therefore, in order to achieve a sufficient reduction ratio, the internal speed reducer of the conventional winch generally needs to use a third-order planetary gear speed reducer in the structural design. However, it is known that the use of the third-order planetary gear speed reducer also requires more components (such as sun gear, planet gear and ring gear), and in order to prevent the winch from being in danger of reverse sliding of the weight due to its own weight caused by sudden power failure during operation, the speed reducer also needs to be designed with a brake system so as to lock the speed reducer when the power failure occurs. Therefore, the winch also uses more components, and further increases the overall manufacturing cost.

Disclosure of Invention

One of the objectives of the present invention is to improve the disadvantages of the prior art, and to provide a speed reducer which can achieve the same or better speed reduction effect with fewer components.

Another object of the present invention is to provide a speed reducer of a winch that has a self-locking function.

Therefore, a speed reducer according to an embodiment of the present invention is provided, which has a differential gear speed reducing mechanism and a planetary speed reducing mechanism. The gear difference reduction mechanism comprises a first inner gear ring, a transmission gear, a sun gear and a plurality of first planet gears. The first inner ring gear is provided with a first inner ring tooth part, the transmission gear and the first inner ring gear are coaxially arranged and comprise a second inner ring tooth part and a first output gear shaft which are oppositely arranged, the second inner ring tooth part is adjacent to the first inner ring tooth part, and the number of teeth of the first inner ring tooth part is different from that of the second inner ring tooth part. The sun gear is arranged in the first inner ring tooth part and the second inner ring tooth part in a driving mode. The first planetary gears are arranged between the sun gear and the first and second inner ring tooth parts, and each first planetary gear completely engages with the sun gear and the first and second inner ring tooth parts at the same time.

The planetary reduction mechanism comprises a second inner gear ring, a planetary support and a plurality of second planetary gears. The second inner gear ring is provided with a third inner ring gear part, the first output gear shaft extends into the second inner gear ring, and the first output gear shaft and the second inner gear ring are coaxially arranged. The planet support is arranged in the second inner gear ring, and a second output gear shaft is arranged on one side of the planet support, which is back to the gear difference speed reducing mechanism. The second planetary gears are rotatably arranged on the planetary carrier and positioned between the first output gear shaft and the third inner ring tooth part, and each second planetary gear is meshed with the first output gear shaft and the third inner ring tooth part.

With the above-described structural design of the speed reducer, since the reduction ratio of the differential gear reduction mechanism is generally larger than that of the planetary reduction mechanism, it is possible to achieve an effective reduction effect by using only one set of differential gear reduction mechanism and one set of planetary reduction mechanism. Compared with the prior art, the speed reducer uses fewer parts and can achieve the same or even better speed reduction effect. In addition, the tooth difference speed reducing mechanism has the self-locking characteristic, so that the speed reducer does not need to be designed with other brake structures in use, and parts needed by the brake structures can be saved.

In addition, the invention also provides a winch which comprises a shell, the speed reducer, a cable reel and a motor. The casing has one opening, the speed reducer is set inside the casing, and the first and the second ring gear are fixed to the casing. One end of the cable spool is connected to the second output pinion so that the cable spool can be driven to rotate by the second output pinion. The motor has a rotating shaft, and the rotating shaft is coaxially and fixedly connected with the sun gear.

In one aspect, the first output gear shaft and the second output gear shaft are both hollow. The rotating shaft of the motor is fixedly connected with the sun gear through the second output gear shaft and the inner part of the first output gear shaft so as to drive the sun gear to rotate.

In another aspect, the outer circumferential surface of the first inner gear ring is provided with at least one first engaging portion, the winch further includes a clutch member disposed in the housing and having a second engaging portion located in the housing, the clutch member being switchable between an engaging position and a non-engaging position (e.g., switchable between the engaging position and the non-engaging position by rotation or movement). When the clutch piece is positioned at the clamping position, the second clamping part can be clamped with the first clamping part, so that the first inner gear ring is fixedly connected with the shell and cannot be rotated; when the clutch piece is located at the non-clamping position, the second clamping part is not clamped with the first clamping part, so that the first annular gear can be rotated, and the gear difference speed reducing mechanism is in an idling state without outputting the speed reducing effect.

In another aspect, the inner wall of the housing is further provided with a ring gear protrusion, and the second inner gear ring is detachably engaged with the ring gear protrusion.

Drawings

The detailed construction, features, assembly or use of the decelerator are described in the following embodiments, however, it should be understood that the embodiments to be described below and the accompanying drawings are only illustrative and should not be used to limit the scope of the present invention, wherein:

FIG. 1 is a perspective view of a winch according to an embodiment of the present invention;

FIG. 2 is an enlarged view of a portion of FIG. 1, with a portion of the cable spool and motor of the winch omitted from illustration;

FIGS. 3 and 4 are exploded views of FIG. 2;

FIG. 5 is a cross-sectional view of FIG. 2;

FIG. 6 is a schematic cross-sectional view from another angle in FIG. 2, with the first casing member omitted;

FIG. 7 is an enlarged view of a portion of FIG. 6;

FIG. 8 is an enlarged perspective view of the clutch member;

FIGS. 9A, 9B, 10A and 10B are schematic views illustrating the actuation of the clutch member, wherein FIGS. 9A and 10A are for explaining the clutch member at the engaging position, and FIGS. 9B and 10B are for explaining the clutch member at the non-engaging position;

fig. 11 is a schematic connection diagram of the second casing member and the second ring gear.

In the above figures, the reference numerals have the following meanings:

1 winch

10 speed reducer

20 tooth difference speed reducing mechanism

21 first ring gear

211 first inner ring tooth part 212 first engaging part

22 drive gear

221 second inner ring tooth 222 first output gear shaft

223 through hole

23 sun gear 24 first planetary gear

25 planet carrier

30 planetary reduction mechanism

31 second ring gear

311 third inner ring tooth part

32 planet carrier

321 second output gear shaft 322 through hole

33 second planetary gear

40 Clutch member

41 second engaging part 42 handle

50 casing

51 first shell 52 second shell

521 ring tooth projection

53 opening

60 cable spool

61 Steel cable 62 hook

70 motor 71 rotating shaft

81 waterproof gasket 82 fixing ring

angle a1-a4

Detailed Description

The technical contents and features of the present invention will be described in detail below with reference to several embodiments, and directional terms such as "upper", "lower", "inner", "outer", "top" and "bottom" referred to in the present specification are only exemplary terms based on a normal use direction and are not intended to limit the scope of claims.

To illustrate the technical features of the present invention in detail, the following embodiments are described with reference to the accompanying drawings, wherein:

as shown in fig. 1 and 2, the winch 1 of the embodiment includes a motor 70, a cable reel 60, a housing 50 and a speed reducer 10 disposed in the housing 50. The motor 70 is provided on one side of the cable reel 60, and the housing 50 together with the speed reducer 10 is provided on the other side of the cable reel 60. The cable spool 60 is hollow and the cable spool 60 is used to wind a cable 61. the end of the cable 61 is provided with a hook 62. the hook 62 can be used to connect a heavy object (such as a vehicle to be rescued).

The housing 50 has a first housing 51, a second housing 52 and an opening 53, the first housing 51 and the second housing 52 are integrally locked by a plurality of screws, and the opening 53 is located on the second housing 52. The motor 70 has a rotating shaft 71, and the rotating shaft 71 extends into the housing 50 through the inside of the cable spool 60 and the opening 53 of the housing 50, thereby driving the reducer 10. The speed reducer 10 has a second output gear shaft 321, and one end of the cable spool 60 extends into the housing 50 through the opening 53 and directly engages with the second output gear shaft 321, so that when the second output gear shaft 321 rotates, the cable spool 60 can be synchronously driven to rotate to wind the cable 61, thereby pulling the heavy object. In addition, the winch 1 is further provided with a clutch member 40, the clutch member 40 is rotatably provided in the housing 50, and one end of the clutch member 40 is inserted into the housing 50. The following paragraphs will describe the specific structure of the reducer 10 and the clutch 40 and the operation thereof in detail.

Please refer to fig. 3-5. The decelerator 10 includes a differential gear deceleration mechanism 20 and a planetary deceleration mechanism 30. The differential gear mechanism 20 is provided in the first casing 51, and the planetary gear mechanism 30 is provided in the second casing 52.

The differential reduction mechanism 20 includes a first ring gear 21, a transmission gear 22, a sun gear 23 and three first planetary gears 24. The first ring gear 21 is rotatably disposed in the first casing 51, and has an inner ring gear portion 211 and an outer ring surface with ten first engaging portions 212 arranged at equal angles. The first inner ring tooth portion 211 has fifty one tooth, and each of the first engaging portions 212 has an arc-groove-shaped structure. The transmission gear 22 is coaxially disposed with the first inner ring gear 21, and structurally includes a second inner ring gear portion 221 and a first output gear shaft 222 disposed oppositely, the second inner ring gear portion 221 is adjacent to the first inner ring gear portion 211, and the first output gear shaft 222 protrudes toward the second casing 52. The second inner ring gear portion 221 has fifty-four teeth and the first output gear shaft 222 has eighteen teeth, so that it can be seen that the number of teeth of the first inner ring gear portion 211 is different from that of the second inner ring gear portion 221. In addition, a through hole 223 is formed in the center of the first output gear shaft 222, and the through hole 223 communicates with the inside of the second inner ring gear portion 221, allowing the rotating shaft 71 to extend into the transmission gear 22 and the inside of the first inner ring gear 21 (see fig. 5).

The sun gear 23 has fifteen teeth, and is coaxially sleeved on the rotating shaft 71 of the motor 70, and the cross section of the rotating shaft 71 is a regular hexagon, so that the sun gear 23 can be driven by the motor 70 to rotate. The sun gear 23 is provided in the first inner ring gear portion 211 and the second inner ring gear portion 221. The three first planetary gears 24 are rotatably provided on the one planet carrier 25, the three first planetary gears 24 are equiangularly provided between the sun gear 23 and the first and second inner

ring gear portions

211, 212, and each first planetary gear 24 completely meshes with the sun gear 23 and the first and second inner

ring gear portions

211, 212 at the same time.

It should be noted that the sun gear 23, the first ring gear 21, and the transmission gear 22 are all coaxially disposed. In addition, a waterproof gasket 81 and a fixing ring 82 are disposed between the differential reduction mechanism 20 and the planetary reduction mechanism 30, and the waterproof gasket 81 is disposed at the boundary between the first casing 51 and the second casing 52 for preventing water from entering the interior of the housing 50 through the boundary between the first casing 51 and the second casing 52. The fixing ring 82 is used to fix the planetary reduction mechanism 30 in the second casing member 52.

Please refer to fig. 6, which is a schematic cross-sectional view of fig. 2 at another angle. As can be seen from the above paragraphs, the number of teeth of the first inner ring tooth 211 (the portion shown with the cross-sectional line) is fifty one and the number of teeth of the second inner ring tooth 221 (most of which are hidden behind the first inner ring tooth 211) is fifty four, and the teeth of the first inner ring tooth 211 and the second inner ring tooth 221 are completely overlapped at three angles a1-a 3. Therefore, when the three first planet gears 24 just engage with the teeth at the three angles a1-a3, the first planet gears 24 are completely engaged with the first and second inner ring teeth 211 and 212 (it should be noted that fig. 6 only illustrates the angle a1-a3 for achieving complete engagement, and the angle for achieving complete engagement may be different in other different designs of the teeth at the first and second

inner ring teeth

211 and 212, and therefore, should not be limited to fig. 6 of this embodiment). Therefore, when the sun gear 23 is driven to rotate by the rotating shaft 71, the sun gear 23 will push the first planet gears 24 to rotate, so that when the first planet gears 24 rotate from the angle a1 to the angle a4, for example, from a fully meshed tooth to another adjacent tooth (see fig. 7), the tooth corresponding to the tooth of the second inner ring tooth portion 221 located at the angle a4 does not completely coincide with the tooth corresponding to the first inner ring tooth portion 211. In the above situation, if the first inner ring gear 21 having the first inner ring gear portion 211 is fixed, since the teeth corresponding to the second inner ring gear portion 221 do not completely overlap the teeth corresponding to the first inner ring gear portion 211, the first planet gears 24 will slightly push the second inner ring gear portion 221, so as to generate a slight rotation of the first output gear shaft 222, thereby achieving the effect of deceleration. In the present embodiment, the reduction gear ratio of the tooth difference reduction mechanism 20 is 79.2.

As to how to fix the first ring gear 21, this embodiment is achieved by the clutch member 40. Please refer to fig. 3, fig. 5 and fig. 8. The clutch member 40 is a first casing 51 rotatably disposed on the housing 50, the clutch member 40 structurally includes a second engaging portion 41 and a handle 42 integrally connected, and the second engaging portion 41 is disposed in the first casing 51. The clutch member 40 can rotate between an engaging position (fig. 9A) and a non-engaging position (fig. 9B), when the clutch member 40 is located at the engaging position, the second engaging portion 41 will engage one of the first engaging portions 212 (fig. 10A), so that the first ring gear 21 is fixed to the first casing member 51; when the clutch 40 is located at the non-engaging position, the second engaging portion 41 will not engage with any of the first engaging portions 212 (see fig. 10B), and the tooth difference deceleration mechanism 20 will be in an idle state without deceleration effect, so that the user can pull the cable 61 out of the cable reel 60.

The planetary reduction mechanism 30 will be described below, please refer back to fig. 2 to 5. The planetary reduction mechanism 30 includes a second ring gear 31, a planet carrier 32 and three second planet gears 33. The second ring gear 31 is fixed in the second casing member 52 (as shown in fig. 5), the inner annular surface of the second ring gear 31 is provided with a third inner annular tooth portion 311, the first output gear shaft 222 extends into the second ring gear 31, and the first output gear shaft 222 and the second ring gear 31 are coaxially arranged. The number of teeth of the third inner ring gear portion 311 is forty-eight. It should be noted that in this embodiment, a ring gear protrusion 521 (see fig. 11) is disposed on an inner wall of the second casing 52, and the second ring gear 31 is fixed to the second casing 52 through a meshing relationship between the second ring gear protrusion 521 and the ring gear protrusion 521, so that the second ring gear 31 can be conveniently assembled in the second casing 52 by a production line, and in terms of part manufacturing, the second casing 52 and the second ring gear 31 can be manufactured by using a powder metallurgy method, respectively, thereby reducing complexity in manufacturing components.

The planet carrier 32 is disposed in the second ring gear 31, a second output gear shaft 321 is disposed on a side of the planet carrier 32 facing away from the tooth difference reduction mechanism 20 (i.e., the second output gear shaft 321 faces the opening 53, see fig. 5), the number of the second output gear shaft 321 is twenty teeth, and a through hole 322 is disposed in the center of the second output gear shaft 321, so that the rotating shaft 71 of the motor 70 is allowed to extend into the first ring gear 21 and the transmission gear 22 through the through hole 322 of the second output gear shaft 321 and the through hole 223 of the first output gear shaft 222. The second planetary gears 33 are rotatably provided on the planetary carrier 32 and positioned between the first output pinion 222 and the third inner ring gear portion 311, the first output pinion 222 is inserted into the planetary carrier 32, the second planetary gears 33 are simultaneously in mesh with the first output pinion 222 and the third inner ring gear portion 311, and the number of teeth of the second planetary gears 33 is fifteen. In the present embodiment, the reduction ratio of the planetary reduction mechanism 30 is 3.42, the total reduction ratio of the winch 1 of the present embodiment is about 270, and the planetary reduction mechanism 30 and the tooth difference reduction mechanism 20 are matched to achieve a proper reduction effect of the winch 1.

In practice, when the user wants to use the winch 1 to pull a heavy object, the user can rotate the clutch member 40 to the non-engaging position (see fig. 9B), and the second engaging portion 41 of the clutch member 40 does not engage with the first engaging portion 212 of the first inner gear ring 21 (see fig. 10B), so that the entire differential reduction mechanism is in an idle state, and the user can pull the cable 61 from the cable spool 60 to hang the cable 61 on the heavy object. Then, the user can rotate the clutch member 40 to the engaging position (see fig. 9A), so that the second engaging portion 41 of the clutch member 40 engages with the first engaging portion 212 of the first ring gear 21 (see fig. 10A), thereby fixing the first ring gear 21, and the user can start the motor 70, rotate the rotating shaft 71 thereof through the motor 70, and gradually wind the cable spool 60 and pull the heavy object under the deceleration of the differential gear mechanism 20 and the planetary reduction mechanism 30.

Since the reduction ratio of the differential gear reduction mechanism 20 is usually larger than that of the planetary reduction mechanism 30, the reduction ratio of the present embodiment, which is obtained by combining one set of differential gear reduction mechanisms 20 and one set of planetary reduction mechanisms 30, is comparable to (even larger than) that of a reduction gear obtained by combining three sets of planetary reduction mechanisms 30. It can be seen that the winch 1 of the present embodiment can achieve the same or even higher reduction ratio with a smaller number of components.

On the other hand, when the motor 70 is suddenly de-energized for any reason, the rotation shaft 71 stops rotating together with the sun gear 23 fitted around the rotation shaft 71, and the first planetary gears 24 of the differential gear mechanism 20 do not rotate at this time. As described in the previous paragraph (please refer to fig. 7), the first planetary gears 24 completely engage the first ring gear 21 and the transmission gear 22 at the same time, and the external force cannot drive the first ring gear 21 and the transmission gear 22 annularly. That is, the tooth difference reduction mechanism 20 of the present embodiment has a self-locking property, and when the motor 70 is powered off, the weight cannot slide reversely due to its own weight, which increases safety in use.

The above-mentioned embodiments are only examples of the present invention, and all equivalent changes and modifications made within the scope of the claims should be covered by the present invention.

Claims

1. A speed reducer, comprising:

a differential gear reduction mechanism, comprising:

a first inner gear ring having a first inner ring gear portion;

a transmission gear, coaxially disposed with the first inner gear ring and including a second inner ring gear portion and a first output gear shaft disposed oppositely, wherein the second inner ring gear portion is adjacent to the first inner ring gear portion, and the number of teeth of the first inner ring gear portion is different from that of the second inner ring gear portion;

the sun gear can be arranged in the first inner ring tooth part and the second inner ring tooth part in a driving way;

a plurality of first planetary gears provided between the sun gear and the first and second inner ring gear portions, each of the first planetary gears completely meshing with the sun gear and the first and second inner ring gear portions at the same time; and

a planetary reduction mechanism, comprising:

the second inner gear ring is provided with a third inner ring gear part, wherein the first output gear shaft extends into the second inner gear ring, and the first output gear shaft and the second inner gear ring are coaxially arranged;

the planet support is arranged in the second inner gear ring, and a second output gear shaft is arranged on one side of the planet support, which is back to the gear difference speed reducing mechanism;

and the plurality of second planet gears are rotatably arranged on a planet carrier and are positioned between the first output gear shaft and the third inner ring tooth part, and each second planet gear is meshed with the first output gear shaft and the third inner ring tooth part.

2. The reducer of claim 1, in combination with a motor having a shaft, the sun gear being coaxially journalled about the shaft.

3. The speed reducer of claim 2, wherein the second output gear shaft and the first output gear shaft are hollow, and the rotating shaft is fixedly connected to the sun gear through the second output gear shaft and the first output gear shaft.

4. A winch, comprising:

a housing having an opening;

a decelerator as claimed in claim 1 disposed within the housing, wherein the first and second inner gear rings are fixedly coupled to the housing;

one end of the cable spool is connected with the second output gear shaft, so that the cable spool can be driven by the second output gear shaft to rotate;

a motor having a rotating shaft coaxially sleeved with the sun gear.

5. The winch of claim 4, wherein the second output gear shaft and the first output gear shaft are hollow, and the rotating shaft is fixed to the sun gear through the second output gear shaft and the first output gear shaft.

6. The winch of claim 4, wherein the outer circumferential surface of the first inner gear ring has at least one first engaging portion, the winch further comprising a clutch member movably disposed in the housing and having a second engaging portion disposed in the housing, the clutch member being movable between an engaging position and a non-engaging position, the second engaging portion engaging the at least one first engaging portion when the clutch member is at the engaging position, such that the first inner gear ring is fixedly coupled to the housing; when the clutch piece is located at the non-clamping position, the second clamping part is not clamped with the at least one first clamping part.

7. The winch of claim 4, wherein the inner wall of the housing further defines a ring gear protrusion, and the second inner gear ring is detachably engaged with the ring gear protrusion.

8. The winch of claim 4, wherein an end of the cable spool extends into the housing through the opening and is connected to the second output pinion such that the cable spool rotates synchronously with the second output pinion.