CN112815051A - Transmission mechanism and gear box - Google Patents

Abstract

The application provides a drive mechanism and gear box relates to transmission technical field, includes: a shaft member; two transmission stages arranged along an axial direction of the shaft member; in a state where the shaft member rotates in the first clock hand direction, a first gear stage of the two gear stages is driven by the shaft member to drive a second gear stage of the two gear stages, so that the transmission mechanism outputs a first speed ratio; in a state where the shaft member rotates in the second clockwise direction, the second transmission stage is driven by the shaft member so that the transmission mechanism outputs a second speed ratio smaller than the first speed ratio. The application provides a drive mechanism, through the rotation of shaft member with different directions, output different speed ratios.

Description

Transmission mechanism and gear box

Technical Field

The application relates to the technical field of transmission, in particular to a transmission mechanism and a gear box.

Background

Conventional gearboxes, such as walking gearboxes, generally output only one speed ratio and therefore cannot be shifted. Thus, the walking gearboxes of the prior art are often faced with practical applications in the dilemma: if the walking gear box adopts a large speed ratio, although the output torque is high, the output rotating speed is low, which can cause the walking speed to be slow; if the walking gearbox uses a small speed ratio, the output torque is low although the output rotational speed is high, which can cause difficulty in load working.

Disclosure of Invention

A first object of the present application is to provide a transmission mechanism to output different speed ratios.

A second object of the present application is to provide a gearbox comprising a transmission as described above.

In a first aspect, the present application provides a transmission mechanism comprising:

a shaft member;

two transmission stages arranged along an axial direction of the shaft member;

in a state where the shaft member is rotated in a first clock hand direction, a first gear stage of the two gear stages is driven by the shaft member to drive a second gear stage of the two gear stages, so that the gear mechanism outputs a first speed ratio;

in a state where the shaft member rotates in a second clockwise direction, the second transmission stage is driven by the shaft member, so that the transmission mechanism outputs a second speed ratio smaller than the first speed ratio.

The shaft member described herein is understood to include a shaft whose axis is a straight line and a crankshaft.

Preferably, any of the gear stages comprises a sun gear.

Preferably, the sun gear is formed with a center hole, and the transmission mechanism further includes:

a first drive assembly disposed between the central bore of the sun gear of the first gear stage and the outer side of the shaft member, the first drive assembly being configured to transmit torque only when the shaft member is rotated in a first clock direction;

a second drive assembly disposed between the central bore of the sun gear of the second gear stage and the outer side of the shaft member, the second drive assembly being configured to transmit torque only when the shaft member is rotated in a second clockwise direction.

Preferably, at least one of the first drive assembly and the second drive assembly is arranged to complete the orientation after assembly to the shaft member.

The orientation referred to herein should be understood to determine the direction in which a drive assembly is capable of transmitting torque when the shaft member is rotated.

Preferably, the first drive assembly and the second drive assembly are both formed as directional clutches.

Preferably, the gear stages are formed as planetary gear stages, any of the planetary gear stages comprising:

a sun gear formed as the sun gear;

the planet wheels are arranged around the sun wheel and meshed with the sun wheel;

a planet carrier for supporting the planet gears;

the transmission mechanism further comprises a gear ring component, and the gear ring component is used for being meshed with the planet gear.

Preferably, the ring gear assembly includes:

the first-stage gear ring is meshed with the planet gear of the first transmission stage;

and the rest stages of gear rings are meshed with the planet gears of the second transmission stage.

Preferably, the transmission mechanism further comprises the remaining transmission stages;

the other transmission stages are arranged between the first transmission stage and the second transmission stage and are driven by the first transmission stage in a state that the shaft member rotates along a first clock hand direction; or

The rest of the transmission stages are arranged on one side of the second transmission stage far away from the first transmission stage, and are driven by the second transmission stage in a state that the shaft member rotates along a second clockwise direction.

Preferably, any of said gear stages comprises:

a secondary gear engaged with the central gear and formed with a central hole;

the secondary shaft component is arranged in the central hole of the secondary gear in a penetrating mode;

the transmission mechanism further includes:

a first secondary drive assembly disposed between the central bore of the secondary gear of the first transmission stage and the outer side of the secondary shaft member and configured to transmit torque only when the first drive assembly transmits torque;

a second secondary drive assembly disposed between the central bore of the secondary gear of the second transmission stage and the outer side of the secondary shaft member and configured to transmit torque only when the second drive assembly transmits torque.

In a second aspect, the present application provides a gearbox comprising a transmission as described above.

The application provides a drive mechanism, through the rotation of shaft member with different directions, output different speed ratios.

In order to make the aforementioned objects, features and advantages of the present application more comprehensible, preferred embodiments accompanied with figures are described in detail below.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present application and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained from the drawings without inventive effort.

FIG. 1 illustrates a schematic diagram of a cross-sectional view of a gearbox provided by an embodiment of the present application.

Fig. 2 shows a schematic diagram of another gear stage provided by an embodiment of the present application.

Reference numerals:

1-third stage sun gear; 2-a second stage sun gear; 3-a first stage sun gear; 4-first stage planets; 5-a first stage planet carrier; 6-first-stage annular gear; 7-a second stage planet wheel; 8-a second stage planet carrier; 9-a second three-level annular gear; 10-third stage planets; 11-third stage planet carrier; 12-a second clutch; 13-a shaft member; 14-a first clutch;

100-first stage sun gear; 110-a second stage sun gear; 120-a primary secondary gear; 130-a second stage secondary gear; 140-a secondary shaft member; 150-first secondary clutch; 160-second secondary clutch.

Detailed Description

The technical solutions of the present application will be described clearly and completely with reference to the accompanying drawings, and it should be understood that the described embodiments are only some embodiments of the present application, but not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.

In the description of the present application, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present application. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.

In the description of the present application, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present application can be understood in a specific case by those of ordinary skill in the art.

In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present application.

The transmission mechanism provided by the embodiment comprises a third-stage sun gear, a second-stage sun gear, a first-stage planet carrier, a first-stage inner gear ring, a second-stage planet gear, a second-stage planet carrier, a second-stage inner gear ring, a third-stage planet gear, a third-stage planet carrier, a second clutch, a shaft member and a first clutch. The structure, connection relationship and operation principle of the aforementioned components will be described in detail with reference to fig. 1.

In order to facilitate the clarification of the concept of the present application, in the following description, the arrangement of the third-stage sun gear 1, the second-stage sun gear 2, the first-stage sun gear 3, the first-stage planet gear 4, the first-stage planet carrier 5, the first-stage ring gear 6, the second-stage planet gear 7, the second-stage planet carrier 8, the second-stage ring gear 9, the third-stage planet gear 10, and the third-stage planet carrier 11 will be described first, including the connection relationship, the relative position relationship, and the like. On this basis, the operation of these components will be further described, and the arrangement of the shaft member 13, the first clutch 14, and the second clutch 12 will be described later.

As shown in fig. 1, fig. 1 shows, in an embodiment, a sectional view of a gear box to which the transmission mechanism is applied, which will be described later after the description of the transmission mechanism. The sectional view is a plane passing through the axis of the shaft member 13 and obtained by cutting the gear box. Referring further to fig. 1, the axis of the shaft member 13 described above extends along the horizontal direction in the drawing, that is, the axial direction of the shaft member 13 is the horizontal direction in the drawing. In addition, the third-stage sun gear 1, the second-stage sun gear 2, and the first-stage sun gear 3 are provided in this order along the axial direction of the shaft member 13 from the left side to the right side in the drawing. The "sun gear" referred to herein (i.e., the third-stage sun gear 1, the second-stage sun gear 2, and the first-stage sun gear 3) is formed as a gear, and may be provided coaxially with a shaft member 13 described below.

On the basis of the technical features described above, further referring to fig. 1, in an embodiment, the number of the first-stage planetary gears 4 may be three (or more), and the first-stage planetary gears 4 are held via the first-stage planetary carrier 5. Specifically, three first-stage planetary wheels 4 may be evenly distributed on the circumference, thereby holding the first-stage sun wheel 3 in the middle. For the first stage carrier 5, the shaft portion may be formed to penetrate the center hole of the first planetary gear. A bearing is further provided between the shaft portion of the first-stage planet carrier 5 and the inner side of the first-stage planet wheel 4, which enables the first-stage planet wheel 4 to rotate around the shaft portion of the first-stage planet carrier 5. Further, the first-stage carrier 5 is connected to the second-stage sun gear 2.

In the embodiment, still referring to fig. 1, three first-stage planetary wheels 4 are all engaged with a first-stage ring gear arranged on the outer side of the three, so that when the first-stage sun wheel 3 rotates, the three first-stage planetary wheels 4 will perform planetary motion around the first-stage sun wheel 3 while driving the first-stage ring gear 6 engaged with them to rotate.

Further, as shown in fig. 1, the above-described first-stage ring gear is connected to a second-stage ring gear, which is described below, so that when three first-stage planetary gears 4 described above perform planetary motion, the first-stage planetary gear carrier 5 supporting them also performs planetary motion, and the first-stage planetary gear carrier 5 is connected to the second-stage sun gear 2, whereby the second-stage sun gear 2 is driven to rotate, and the second-stage planetary gears 7 are further driven by the second-stage sun gear 2.

In the embodiment, the second stage sun gear 2 is held in a similar manner to the first stage sun gear 3, i.e., the second stage sun gear 2 may also be in mesh with three (or more) second stage planetary gears 7 to be held in the middle by the second stage planetary gears 7. Similarly, the second-stage planet gear 7 is also correspondingly provided with a second-stage planet carrier 8, which has already been mentioned in the above description, and here, the matching way of the second-stage planet gear 7 and the second-stage planet carrier 8 is the same as the matching way of the first-stage planet gear 4 and the first-stage planet gear 4, and in addition, the second-stage planet carrier 8 is connected with the third-stage sun gear 1, so as to drive the third-stage sun gear 1 to rotate, which is not described again here.

On the basis of this, the three second-stage planet gears 7 are all meshed with a second-third-stage ring gear 9 arranged on their outer side, where the second-third-stage ring gear 9 is also meshed with a third-stage planet gear 10 described below, and is therefore referred to as a second-third-stage ring gear 9. As shown in fig. 1, as mentioned above, three third-stage planetary gears 10 are provided outside the third-stage sun gear 1 and held by the third-stage carrier 11. Furthermore, three third-stage planet gears 10 are each in mesh with the aforementioned second-stage ring gear 9, and in the exemplary embodiment, the third-stage planet gears 10 can be arranged to no longer perform a planetary motion, that is to say the third-stage planet carrier 11 can no longer perform a planetary motion, via the transmission of the first two-stage planet gears and their respective sun gears.

However, if the above co-operating planet carrier, planet wheels and sun wheel are to be considered as one gear stage, the number of gear stages may in fact not be limited to three as mentioned above, for example may be fewer than two, or may be more than three.

On the basis of the technical features described above, the mounting manner and the operating principle of the shaft member 13, the first clutch 14, and the second clutch 12 will be described in detail below.

Still referring to fig. 1, in the example given in fig. 1, all three of the first stage sun gear 3, the second stage sun gear 2, and the third stage sun gear 1 are formed with center holes. The shaft member 13 penetrates through the three center holes, and on this basis, for convenience of description, the center hole formed by the first-stage sun gear 3 is defined as a first center hole, and the center hole formed by the second-stage sun gear 2 is defined as a second center hole. Based on such a definition, the first clutch 14 is disposed between an inner portion of the first center hole and an outer portion of the first shaft member 13, and the second clutch 12 is disposed between an inner portion of the second center hole and an outer portion of the first shaft member 13.

In the embodiment, although the specific structure of the first clutch 14 and the second clutch 12 is not shown, it is understood that a directional clutch may be employed for both the first clutch 14 and the second clutch 12. That is, for example, with the first clutch 14, the first clutch 14 transmits the torque of the shaft member 13 to the first-stage sun gear 3 only when the shaft member 13 rotates in a predetermined direction, for example, clockwise, whereas the first clutch 14 separates the shaft member 13 and the first-stage sun gear 3 from each other if the shaft member 13 rotates in a direction opposite to the predetermined direction, for example, counterclockwise. Preferably, the first clutch 14 and the second clutch 12 are installed to complete their respective corresponding orientations without additional electrical or hydraulic control after the transmission is assembled, so that the compactness of the transmission is effectively improved and the occupied space is small because electrical and hydraulic equipment is not required to be arranged in the transmission. In addition, the transmission mechanism is reduced in complexity, light in weight and convenient to mount and dismount.

The above-mentioned clockwise direction and counterclockwise direction refer to the movement direction of the shaft member 13 as viewed along the axis of the shaft member 13. For example, when viewed along the axis to the right on the left side of the shaft member 13, the rotational movement of the shaft member 13 about the axis may be understood as a clockwise movement and a counterclockwise movement.

Similarly, in the embodiment, the second clutch 12 transmits torque in a manner similar to that of the first clutch 14, but differs in that the second clutch 12 is disposed in an opposite manner with respect to the first clutch 14. That is, when the shaft member 13 rotates in the clockwise direction, the first clutch 14 brings the shaft member 13 into engagement with the first-stage sun gear 3, thus transmitting the torque of the shaft member 13 to the first-stage sun gear 3, while the second clutch 12 and the second-stage sun gear 2 are both free to rotate; conversely, when the shaft member 13 rotates in the counterclockwise direction, the second clutch 12 brings the shaft member 13 into engagement with the second-stage sun gear 2, thus transmitting the torque of the shaft member 13 to the second-stage sun gear 2.

For convenience of description, the case where the shaft member 13 rotates in the clockwise direction may be referred to as normal rotation of the shaft member 13, and the case where the shaft member 13 rotates in the counterclockwise direction may be referred to as reverse rotation of the shaft member 13. Based on the above description, it can be seen that when the shaft member 13 rotates in the forward direction, the three gear stages all participate in the torque transmission process, and finally the rotational speed output via the second-stage ring gear 9 and the first-stage ring gear 6 is low (i.e., the transmission mechanism has a large speed ratio), but the output torque is large; when the shaft element 13 is reversed, only the second gear stage and the third gear stage are involved in the torque transmission process (the first gear stage is subject to the follow-up movement and is not involved in the torque transmission), and finally the rotational speed output via the two-stage ring gear 9 is high (i.e. the transmission mechanism has a small speed ratio), but the output torque is small. The transmission mechanism thus provided in the present embodiment achieves output at different speed ratios only by the normal rotation and reverse rotation of the shaft member 13.

However, without being limited thereto, the position in which the second clutch is disposed is not limited to the position described above, and in fact, as an alternative, the second clutch may be disposed between the central bore of the third stage sun gear and the outer side portion of the shaft member, such that only the third transmission stage participates in the torque transmission process when the shaft member is reversed.

As shown in fig. 2, fig. 2 shows a schematic diagram of an embodiment of another gear stage provided by the present embodiment. In the example given in fig. 2, the same reference numerals are still used for the same components. As shown in fig. 2, the shaft member 13 is inserted through the center hole of the first-stage sun gear 100 and the center hole of the second-stage sun gear 110, and the first clutch 14 and the second clutch 12 are respectively disposed between the center hole of the first-stage sun gear 100 and the outer side portion of the shaft member 13 and between the center hole of the second-stage sun gear 110 and the outer side portion of the shaft member 13.

The transmission also includes a first stage secondary gear 120 in mesh with the first stage sun gear 100 and a second stage secondary gear 130 in mesh with the second stage sun gear 110. Both the first-stage secondary gear 120 and the second-stage secondary gear 130 are formed with center holes through which the secondary shaft member 140 is inserted. On this basis, the transmission mechanism further includes a first secondary clutch 150 and a second secondary clutch 160 which are respectively disposed between the center hole of the first-stage secondary gear 120 and the outer side portion of the secondary shaft member 140 and between the center hole of the second-stage secondary gear 130 and the outer side portion of the secondary shaft member 140. Both the first secondary clutch 150 and the second secondary clutch 160 may employ the same clutches as the first clutch 14 and the second clutch 12 described above.

On this basis, when the shaft member 13 rotates in the clockwise direction (the direction can be referred to as defined above), the first clutch 14 transmits the torque to the first-stage sun gear 100, and the second clutch 12 separates the second-stage sun gear 110 from the second-stage sun gear 110, so that the first-stage sun gear 100 transmits the torque to the first-stage secondary gear 120, and the first-stage secondary gear 120 transmits the torque to the secondary shaft member 140 via the first-stage clutch 150. At this time, the second secondary clutch 160 separates the secondary shaft member 140 from the second secondary gear, so that the second secondary gear does not affect the transmission, and the torque is finally output through the secondary shaft member 140.

Conversely, when the shaft member 13 rotates in the counterclockwise direction, the second clutch 12 transmits the torque to the second stage sun gear 110, and the first clutch 14 separates the first stage sun gear 100 from the first stage sun gear 100, so that the second stage sun gear 110 transmits the torque to the second stage secondary gear 130, and the second stage secondary gear 130 transmits the torque to the secondary shaft member 140 via the second stage clutch 160. At this time, the first secondary clutch 150 separates the secondary shaft member 140 from the first secondary gear, so that the first secondary gear does not affect the transmission, and the torque is finally output through the secondary shaft member 140. In this manner, the forward rotation and the reverse rotation of the shaft member 13 can output different speed ratios.

The present embodiment also provides a gearbox comprising a transmission as described above, which gearbox may for example be formed as a walking gearbox. The gear box can provide large torque to adapt to load working occasions and can also provide high rotating speed to adapt to occasions needing quick running through positive and negative rotation.

The above description is only a preferred embodiment of the present application, and not intended to limit the scope of the present application, and all changes that can be made in the details of the description and drawings, or directly/indirectly implemented in other related technical fields, are intended to be embraced therein without departing from the spirit of the present application.

Claims (10)

1. A transmission mechanism, characterized in that it comprises:

a shaft member;

two transmission stages arranged along an axial direction of the shaft member;

in a state where the shaft member is rotated in a first clock hand direction, a first gear stage of the two gear stages is driven by the shaft member to drive a second gear stage of the two gear stages, so that the gear mechanism outputs a first speed ratio;

in a state where the shaft member rotates in a second clockwise direction, the second transmission stage is driven by the shaft member, so that the transmission mechanism outputs a second speed ratio smaller than the first speed ratio.

2. The transmission mechanism as recited in claim 1, wherein any of the transmission stages comprises a sun gear.

3. The transmission mechanism as claimed in claim 2, wherein the sun gear is formed with a central bore, the transmission mechanism further comprising:

a first drive assembly disposed between the central bore of the sun gear of the first gear stage and the outer side of the shaft member, the first drive assembly being configured to transmit torque only when the shaft member is rotated in a first clock direction;

a second drive assembly disposed between the central bore of the sun gear of the second gear stage and the outer side of the shaft member, the second drive assembly being configured to transmit torque only when the shaft member is rotated in a second clockwise direction.

4. Transmission mechanism according to claim 3,

at least one of the first drive assembly and the second drive assembly is configured to complete the orientation upon assembly to the shaft member.

5. The transmission mechanism as claimed in claim 4, wherein the first drive assembly and the second drive assembly are each formed as a directional clutch.

6. A transmission mechanism as claimed in claim 3, wherein the transmission stages are formed as planetary transmission stages, any of which planetary transmission stages comprises:

a sun gear formed as the sun gear;

the planet wheels are arranged around the sun wheel and meshed with the sun wheel;

a planet carrier for supporting the planet gears;

the transmission mechanism further comprises a gear ring component, and the gear ring component is used for being meshed with the planet gear.

7. The transmission mechanism as recited in claim 6, wherein the ring gear assembly comprises:

the first-stage gear ring is meshed with the planet gear of the first transmission stage;

and the rest stages of gear rings are meshed with the planet gears of the second transmission stage.

8. The transmission mechanism as claimed in claim 1, characterized in that it further comprises the remaining transmission stages;

the other transmission stages are arranged between the first transmission stage and the second transmission stage and are driven by the first transmission stage in a state that the shaft member rotates along a first clock hand direction; or

The rest of the transmission stages are arranged on one side of the second transmission stage far away from the first transmission stage, and are driven by the second transmission stage in a state that the shaft member rotates along a second clockwise direction.

9. Transmission mechanism according to claim 3,

any of the gear stages comprises:

a secondary gear engaged with the central gear and formed with a central hole;

the secondary shaft component is arranged in the central hole of the secondary gear in a penetrating mode;

the transmission mechanism further includes:

a first secondary drive assembly disposed between the central bore of the secondary gear of the first transmission stage and the outer side of the secondary shaft member and configured to transmit torque only when the first drive assembly transmits torque;

a second secondary drive assembly disposed between the central bore of the secondary gear of the second transmission stage and the outer side of the secondary shaft member and configured to transmit torque only when the second drive assembly transmits torque.

10. A gearbox, characterized in that the gearbox comprises a transmission according to any of claims 1-9.

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