A transmission mechanism with multiple reverse gears and reduced distance

Abstract

The present invention provides a transmission mechanism with multiple reverse gears of a step-down type, comprising an input shaft, a front output shaft, a rear output shaft, an intermediate shaft, a planetary row P1, a planetary row P2, a planetary row P3 and a planetary row P4, wherein the planetary row P1 sun gear, the planetary row P2 sun gear and the planetary row P3 sun gear are connected in parallel to the input shaft, the planetary row P1 planet carrier is connected to the planetary row P2 ring gear by a spline, the planetary row P2 planet carrier, the planetary row P4 sun gear and the planetary row P3 ring gear are connected by splines respectively, the planetary row P3 planet carrier is also connected in parallel to the planetary row P4 ring gear and then connected to one end of the intermediate shaft, the other end of the intermediate shaft is sequentially meshed with multiple gears in series, and the front output shaft and the rear output shaft are respectively connected to the last gear. By adopting the technical solution of the present invention, the large bearing capacity of the internal meshing teeth and the entire accommodating space of the internal ring gear can be fully utilized, so that the structure is more compact, the transmission ratio is large, and it has the advantages of stable movement, strong impact resistance and vibration resistance, etc.

Description

Technical Field

[0001] The invention belongs to the technical field of transmission mechanisms, in particular to a step-down multi-reverse transmission mechanism. Background Art

[0002] At present, the speed change mechanism is widely used in various vehicles and machine tools. The speed change mechanism is an important component in these mechanical equipment. With the development of technology, the existing speed change mechanism has more and more speed gears. However, with the continuous increase in the number of gears, the number of internal parts of the speed change mechanism will inevitably increase, making the structure of the speed change mechanism increasingly complicated, larger and heavier, and people's requirements for the control flexibility of construction machinery such as forklifts, cranes, and bulldozers are also getting higher and higher. Correspondingly, the requirements for the number of gears are also increasing. The power input and output of the existing speed change mechanism are often not at the same height, and there is a requirement for distance reduction. It has front and rear output functions. The transmission should also ensure that the forklift has high power and economy, the axial size should be as small as possible, the transmission efficiency is high, and there is no noise. At present, the fixed-axis structure is commonly used in China, but the fixed-axis speed change mechanism is large in size and weight, and most of them are imported, with high costs, thereby increasing production costs. Summary of the invention

[0003] In order to solve the above technical problems, the present invention provides a transmission mechanism with multiple reverse gears and a step-down type.

[0004] The present invention is achieved through the following technical solutions.

[0005] The present invention provides a transmission mechanism with multiple reverse gears of a step-down type, comprising an input shaft, a front output shaft, a rear output shaft, an intermediate shaft, a planetary row P1, a planetary row P2, a planetary row P3 and a planetary row P4, wherein the planetary row P1, the planetary row P2, the planetary row P3 and the planetary row P4 all comprise a sun gear, a planetary wheel meshed with the corresponding sun gear, a planetary carrier connecting all the planetary wheels in the planetary row together and a ring gear meshed with the corresponding planetary wheels, the planetary row P1 sun gear, the planetary row P2 sun gear and the planetary row P3 sun gear are connected in parallel to the input shaft, the planetary carrier of the planetary row P1 is connected to the ring gear of the planetary row P2 through a spline, the planetary carrier of the planetary row P2 and the sun gear of the planetary row P4 are connected to the ring gear of the planetary row P3 through a spline respectively, the planetary carrier of the planetary row P3 is also connected in parallel to the ring gear of the planetary row P4 and then connected to one end of the intermediate shaft, the other end of the intermediate shaft is meshed with a plurality of gears in series in sequence, and the front output shaft and the rear output shaft are respectively connected to the last gear.

[0006] The planetary gear P2 and the planetary gear P3 are connected in parallel, and then connected in series with the C1 clutch and then connected to the input shaft.

[0007] The sun gear of the planetary row P1 is first connected in parallel with the planetary row P2 carrier, then connected in series with the C2 clutch, and then connected to the input shaft.

[0008] The planetary gear P1 ring is also connected to a C3 brake.

[0009] The planetary gear P2 ring is also connected to a C4 brake.

[0010] The planetary gear P3 ring is also connected to a C5 brake.

[0011] The planetary gear P4 planet carrier is also connected to the C6 brake.

[0012] The planet carrier of the planet row P3 is connected in parallel with the ring gear of the planet row P4 and then connected to the intermediate shaft through a spline.

[0013] The intermediate shaft is connected to the gear via a spline.

[0014] The beneficial effects of the present invention are as follows: by adopting the technical solution of the present invention and a planetary gear shifting structure, as many components in the gear shifting mechanism as possible are meshed together in an internal meshing manner, which has the advantages of compact structure, small size, light weight, etc. In addition, it also has the transmission characteristics of planetary motion and power splitting, and can make full use of the large load-bearing capacity of the internal meshing teeth and the entire accommodating space of the inner gear ring, so that its structure is more compact, the transmission ratio is large, and it has the advantages of smooth movement, strong impact and vibration resistance, etc. The planetary gears are specially arranged and combined, and controlled by a number of hydraulic clutches or hydraulic brakes, so that the gear shifting mechanism can output multiple forward gears and reverse gears, and the impact during gear shifting is reduced, and different gears can be selected according to needs. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 It is a structural schematic diagram of the present invention.

[0016] In the figure: 1-C1 clutch, 2-C2 clutch, 3-planetary row P1 sun gear, 4-planetary row P1 planet carrier, 5-planetary row P1 ring gear, 6-C3 brake, 7-planetary row P2 ring gear, 8-C4 brake, 9-planetary row P2 planet carrier, 10-C5 brake, 11-planetary row P3 ring gear, 12-C6 brake, 13-planetary row P4 planet carrier, 14-planetary row P4 ring gear, 15-planetary row P4 sun gear, 16-intermediate shaft, 17-gear, 20-rear output shaft, 21-front output shaft, 22-planetary row P3 planet carrier, 23-planetary row P3 sun gear, 24-planetary row P2 sun gear, 25-input shaft. DETAILED DESCRIPTION

[0017] The technical solution of the present invention is further described below, but the scope of protection claimed is not limited to the description.

[0018] like Figure 1 As shown, the present invention provides a downshift type multi-reverse gear transmission mechanism, comprising an input shaft 25, a front output shaft 21, a rear output shaft 20, an intermediate shaft 16, a planetary row P1, a planetary row P2, a planetary row P3 and a planetary row P4, wherein the planetary row P1, the planetary row P2, the planetary row P3 and the planetary row P4 each comprise a sun gear, a planetary gear meshing with a corresponding sun gear, a planetary carrier connecting all the planetary gears in the planetary row together and a gear ring meshing with the corresponding planetary gear, the sun gear 3 of the planetary row P1, the sun gear 24 of the planetary row P2 It is connected to the input shaft 25 after being connected in parallel with the planetary row P3 sun gear 23, the planetary row P1 planet carrier 4 is connected to the planetary row P2 ring gear 7 through a spline, the planetary row P2 planet carrier 9, the planetary row P4 sun gear 15 and the planetary row P3 ring gear 11 are respectively connected through splines, the planetary row P3 planet carrier 22 is also connected in parallel with the planetary row P4 ring gear 14 and then connected to one end of the intermediate shaft 16, the other end of the intermediate shaft 16 is meshed with multiple gears 17 in series in sequence, and the front output shaft 21 and the rear output shaft 20 are respectively connected to the last gear 17.

[0019] Furthermore, the planetary gear P2 sun gear 24 is connected in parallel with the planetary gear P3 sun gear 23, and then connected in series with the C1 clutch 1, and then connected to the input shaft 25. The planetary gear P1 sun gear 3 is also connected in parallel with the planetary gear P2 planet carrier 9, and then connected in series with the C2 clutch 2, and then connected to the input shaft 25.

[0020] In addition, the planetary gear P1 ring gear 5 is also connected to the C3 brake 6. The planetary gear P2 ring gear 7 is also connected to the C4 brake 8. The planetary gear P3 ring gear 11 is also connected to the C5 brake 10. The planetary gear P4 carrier 13 is also connected to the C6 brake 12. The planetary gear P3 carrier 22 is connected in parallel with the planetary gear P4 ring gear 14 and is connected to the intermediate shaft 16 through a spline. The number of gears 17 is 3. The intermediate shaft 16 is connected to the gear 17 through a spline. The front output shaft 21 and the rear output shaft 20 are respectively connected to the gear 17 through a spline.

[0021] Thereby, the sun gear 3 of planet row P1 drives the planetary gears in the planet row P1 planet carrier 4, and the planetary gears in the planet row P1 planet carrier 4 drive the planetary gear ring 5 of planet row P1; the sun gear 24 teeth of planet row P2 drives the planetary gears in the planet row P2 planet carrier 9, and the planetary gears in the planet row P2 planet carrier 9 drive the planetary gear ring 7 of planet row P2; the sun gear 23 of planet row P3 drives the planetary gears in the planet row P3 planet carrier 22, and the planetary gears in the planet row P3 planet carrier 22 drive the sun gear 15 of planet row P4; the sun gear 15 of planet row P4 drives the planetary gears in the planet row P4 planet carrier, and the planetary gears in the planet row P4 planet carrier drive the planetary gear ring of planet row P4.

[0022] The technical solution of the present invention adopts a planetary gear shifting structure, and as many components in the gear shifting mechanism as possible are meshed together in an internal meshing manner, which has the advantages of compact structure, small size, light weight, etc. In addition, it also has the transmission characteristics of planetary motion and power splitting, and can fully utilize the large load-bearing capacity of the internal meshing teeth and the entire accommodating space of the inner gear ring to make its structure more compact, with a large transmission ratio, and has the advantages of smooth movement, strong impact and vibration resistance, etc. The planetary gears are specially arranged and combined, and controlled by a number of hydraulic clutches or hydraulic brakes, so that the gear shifting mechanism can output multiple forward gears and reverse gears, and the impact during gear shifting is reduced, and different gears can be selected according to needs.

[0023] Using the technical solution of the present invention, the gear shifting operation process is as follows:

[0024] Neutral: C1 clutch 1 is engaged, other clutches and brakes are not engaged, and there is no power output, which is neutral.

[0025] 1st gear: C1 clutch 1 is engaged, C6 brake 12 is engaged, C1 clutch 1 is engaged, driving the planetary row P3 sun gear 23 to rotate together, the planetary row P3 sun gear 23 drives the planetary wheels in the planetary row P3 planet carrier 22 to rotate, the planetary wheels in the planetary row P3 planet carrier 22 drive the planetary row P3 ring gear 11 to rotate, the planetary row P3 ring gear 11 drives the planetary row P4 sun gear 15 to rotate together, the planetary row P4 sun gear 15 drives the planetary wheels in the planetary row P4 planet carrier 13 to rotate.

[0026] The C6 brake 12 is engaged, the planetary gear P4 carrier 13 is fixed, the planetary gears in the planetary gear P4 carrier 13 drive the planetary gear P4 ring 14 to rotate, and the planetary gear P4 ring 14 drives the intermediate shaft 16 and the gear 17 to rotate together. After several gears 17 are meshed and transmitted, the rear output shaft 20 and the front output shaft 21 are driven to rotate together to achieve the 1st gear.

[0027] 2nd gear; C1 clutch 1 is engaged, C5 brake 10 is engaged, C1 clutch 1 is engaged to drive the planetary row P3 sun gear 23 to rotate together, the planetary row P3 sun gear 23 drives the planetary wheels in the planetary row P3 planet carrier 22 to rotate, C5 brake 10 is engaged to fix the planetary row P3 ring gear 11, the planetary wheels in the planetary row P3 planet carrier 22 drive the planetary row P3 planet carrier 22 to rotate, the planetary row P3 planet carrier 22 drives the intermediate shaft 16 and the gear 17 to rotate together, after multiple gears 17 are meshed and transmitted, finally drives the rear output shaft 20 and the front output shaft 21 to rotate together, realizing 2nd gear.

[0028] 3rd gear: C1 clutch 1 is engaged, C4 brake 8 is engaged. The engagement of C1 clutch 1 drives the planetary gear P2 sun gear 24 and the planetary gear P3 sun gear 23 to rotate together, and the planetary gear P2 sun gear 24 drives the planetary gears in the planetary gear P2 planet carrier 9 to rotate.

[0029] The C4 brake 8 is engaged to fix the planetary gear ring 7 of the planetary gear row P2, and the planetary gears in the planetary gear row P2 carrier 9 drive the planetary gear row P2 carrier 9 to rotate, and the planetary gear row P2 carrier 9 drives the planetary gear ring 11 of the planetary gear row P3 to rotate together. Due to the speed difference between the planetary gear ring 11 of the planetary gear row P3 and the planetary gear P3 sun gear 23, the planetary gears drive the planetary gear row P3 carrier 22 to rotate, and the planetary gear row P3 carrier 22 drives the intermediate shaft 16 and the gear 17 to rotate together. After several gears 17 are meshed and transmitted, the rear output shaft 20 and the front output shaft 21 are finally driven to rotate together to achieve the 3rd gear.

[0030] 4th gear; C1 clutch 1 is engaged, C3 brake 6 is engaged, C1 clutch 1 is engaged to drive planetary row P1 sun gear 3, planetary row P2 sun gear 24, planetary row P3 sun gear 23 to rotate together, planetary row P1 sun gear 3 drives the planetary wheels in planetary row P1 planet carrier 4 to rotate, C3 brake 6 is engaged to fix the planetary row P1 ring gear 5, the planetary wheels of planetary row P1 planet carrier 4 drive the planetary row P1 planet carrier 4 to rotate, and the planetary row P1 planet carrier 4 drives the planetary row P2 ring gear 7 to rotate together.

[0031] The sun gear 24 of planetary row P2 drives the planetary gears in the planetary row P2 carrier 9 to rotate. Due to the speed difference between the ring gear 7 of planetary row P2 and the sun gear 24 of planetary row P2, the planetary gears in the planetary row P2 carrier 9 drive the planetary row P2 carrier 9 to rotate, and the planetary row P2 carrier 9 drives the planetary row P3 ring gear 11 to rotate together.

[0032] The planetary row P3 sun gear 23 drives the planets in the serial planetary row P3 planet carrier 22 to rotate. Due to the speed difference between the planetary row P3 ring gear 11 and the planetary row P3 sun gear 23, the planetary gears in the planetary row P3 planet carrier 22 rotate, and the planetary row P3 planet carrier 22 drives the intermediate shaft 16 and the gear 17 to rotate together. After several gears 17 are meshed and transmitted, it finally drives the rear output shaft 20 and the front output shaft 21 to rotate together to achieve 4th gear.

[0033] 5th gear; C1 clutch 1 is engaged, C2 clutch 2 is engaged, C1 clutch 1 and C2 clutch 2 are engaged, driving the planetary gear P2 carrier 9, planetary gear P3 ring gear 11, and planetary gear P3 sun gear 23 to rotate together, and the planetary gear P3 carrier 22 rotates at the same speed, and the planetary gear P3 carrier 22 drives the intermediate shaft 16 and gear 17 to rotate together, and after several gears 17 are meshed and transmitted, finally drives the rear output shaft 20 and the front output shaft 21 to rotate together, realizing 5th gear.

[0034] 6th gear; C2 clutch 2 is engaged, C3 brake 6 is engaged, C2 clutch 2 is engaged, driving planetary row P2 planet carrier 9 and planetary row P3 ring gear 11 to rotate together, C3 brake 6 is engaged, planetary row P1 ring gear 5 is fixed, planetary row P1 sun gear 3 drives the planetary wheels in planetary row P1 planet carrier 4 to rotate, the planetary wheels in planetary row P1 planet carrier 4 drive planetary row P1 planet carrier 4 to rotate, planetary row P1 planet carrier 4 drives planetary row P2 ring gear 7 to rotate together, due to the differential between planetary row P2 ring gear 7 and planetary row P2 planet carrier 9, the planetary row P2 sun gear 24 is driven to rotate, and the planetary row P3 sun gear 23 is driven to rotate together.

[0035] Due to the differential between the planetary gear ring 11 of the planetary gear row P3 and the sun gear 23 of the planetary gear row P3, the planetary gear ring 11 of the planetary gear row P3 drives the planetary gears in the planetary gear row P3 carrier 22 to rotate, and the planetary gear row P3 carrier 22 drives the intermediate shaft 16 and the gear 17 to rotate together. After several gears 17 are meshed and transmitted, it finally drives the rear output shaft 20 and the front output shaft 21 to rotate together to achieve 6th gear.

[0036] 6th gear; C2 clutch 2 is engaged, C4 brake 8 is engaged, C2 clutch 2 is engaged and drives planetary gear P2 carriers 9 and 11 to rotate together, C4 brake 8 is engaged, planetary gear P2 ring gear 7 is fixed, planetary gear P2 carrier 9 rotates, driving the planetary gears in planetary gear P2 carrier 9 to rotate, the planetary gears in planetary gear P2 carrier 9 drive planetary gear P2 sun gear 24 to rotate, and drive planetary gear P3 sun gear 23 to rotate together.

[0037] Due to the differential between the planetary gear ring 11 of the planetary gear row P3 and the planetary gear sun gear 23 of the planetary gear row P3, the planetary gear ring 11 of the planetary gear row P3 drives the planetary gears in the planetary gear carrier 22 to rotate, and drives the planetary gear carrier 22 of the planetary gear row P3 to rotate. The planetary gear carrier 22 of the planetary gear row P3 drives the intermediate shaft 16 and the gear 17 to rotate together. After several gears 17 are meshed and transmitted, it finally drives the rear output shaft 20 and the front output shaft 21 to rotate together to achieve 7th gear.

[0038] Reverse gear 1; C3 brake 6 is engaged, C5 brake 10 is engaged, C3 brake 6 is engaged, planetary row P1 ring gear 5 is fixed, planetary row P1 sun gear 3 drives the planetary wheels in planetary row P1 planet carrier 4 to rotate, the planetary wheels in planetary row P1 planet carrier 4 drive planetary row P1 planet carrier 4 to rotate, and planetary row P1 planet carrier 4 drives planetary row P2 ring gear 7 to rotate together.

[0039] The planetary gear ring 7 of planetary row P2 drives the planetary gears in the planetary row P2 carrier 9 to rotate, and drives the planetary row P2 carrier 9 to rotate. The planetary row P2 carrier 9 drives the planetary row P3 ring gear 11 to rotate together. The planetary gears in the planetary row P2 carrier 9 drive the planetary row P2 sun gear 24 to rotate in the opposite direction. The planetary row P2 sun gear 24 drives the planetary row P3 sun gear 23 to rotate together.

[0040] Due to the differential between the planetary gear P3 sun gear 23 and the planetary gear P3 ring gear 11, the planetary gear P3 carrier 22 rotates in the opposite direction, and the planetary gear P3 carrier 22 drives the intermediate shaft 16 and the gear 17 to rotate together. After several gears 17 are meshed and transmitted, the rear output shaft 20 and the front output shaft 21 are finally driven to rotate together to achieve reverse gear 1.

[0041] Reverse gear 2; C2 clutch 2 is engaged, C6 brake 12 is engaged, C6 brake 12 is engaged, planetary row P4 planet carrier 13 is fixed, C2 clutch 2 is engaged, driving planetary row P2 planet carrier 9, 11, 15 to rotate together, planetary row P4 sun gear 15 drives the planetary gears in planetary row P4 planet carrier 13 to rotate in the opposite direction, the planetary gears in planetary row P4 planet carrier 13 drive the planetary row P4 ring gear 14 to rotate in the same direction, the planetary row P4 ring gear 14 drives the intermediate shaft 16 and gear 17 to rotate together, after several gears 17 are meshed and transmitted, finally drives the rear output shaft 20 and the front output shaft 21 to rotate together, realizing reverse gear 2.

[0042] Reverse gear 3; C3 brake 6 is engaged, C6 brake 12 is engaged, C3 brake 6 is engaged, planetary row P1 ring gear 5 is fixed, planetary row P1 sun gear 3 drives the planetary wheels in planetary row P1 planet carrier 4 to rotate, the planetary wheels in planetary row P1 planet carrier 4 drive planetary row P1 planet carrier 4 to rotate, planetary row P1 planet carrier 4 drives planetary row P2 ring gear 7 to rotate together, planetary row P2 ring gear 7 drives the planetary wheels in planetary row P2 planet carrier 9 to rotate in the same direction, the planetary wheels in planetary row P2 planet carrier 9 simultaneously drive planetary row P2 planet carrier 9 to rotate, planetary row P2 planet carrier 9 drives planetary row P3 ring gear 11 and planetary row P4 sun gear 15 to rotate together.

[0043] The C6 brake 12 is engaged, the planetary gear P4 carrier 13 is fixed, the planetary gear P4 sun gear 15 drives the planetary gears in the planetary gear P4 carrier 13 to rotate, the planetary gears in the planetary gear P4 carrier 13 drive the planetary gear P4 ring gear 14 to rotate in the opposite direction, the planetary gear P4 ring gear 14 drives the intermediate shaft 16 and the gear 17 to rotate together, and after several gears 17 are meshed and transmitted, finally drives the rear output shaft 20 and the front output shaft 21 to rotate together, realizing reverse gear 3.

Claims

1. A step-down multi-reverse transmission mechanism, comprising an input shaft (25), a front output shaft (21), a rear output shaft (20), an intermediate shaft (16), a planetary row P1, a planetary row P2, a planetary row P3 and a planetary row P4, wherein the planetary row P1 comprises a sun gear (3), planetary wheels meshing with the corresponding sun gear (3), a planetary carrier (4) connecting all the planetary wheels in the planetary row P1 together, and a ring gear (5) meshing with the corresponding planetary wheels; the planetary row P2 comprises a sun gear (24), planetary wheels meshing with the corresponding sun gear (24), a planetary carrier (4) connecting all the planetary wheels in the planetary row P1 together, and a ring gear (5) meshing with the corresponding planetary wheels; The planetary gears in the planetary gear row P2 are connected together by a planet carrier (9) and a ring gear (7) meshing with the corresponding planetary gears; the planetary gear row P3 includes a sun gear (23), a planetary gear meshing with the corresponding sun gear (23), a planet carrier (22) connecting all the planetary gears in the planetary gear row P3 together, and a ring gear (11) meshing with the corresponding planetary gears; the planetary gear row P4 includes a sun gear (15), a planetary gear meshing with the corresponding sun gear (15), a planet carrier (13) connecting all the planetary gears in the planetary gear row P4 together, and a ring gear (11) meshing with the corresponding planetary gears. The sun gear (3) of the planetary row P1, the sun gear (24) of the planetary row P2 and the sun gear (23) of the planetary row P3 are connected in parallel and then connected to the input shaft (25); the planet carrier (4) of the planetary row P1 and the ring gear (7) of the planetary row P2 are connected via splines; the planet carrier (9) of the planetary row P2, the sun gear (15) of the planetary row P4 and the ring gear (11) of the planetary row P3 are connected via splines respectively; the planet carrier (22) of the planetary row P3 is also connected in parallel with the ring gear (14) of the planetary row P4 and then connected to the intermediate shaft (16). The front output shaft (21) and the rear output shaft (20) are respectively connected to the last gear (17); the sun gear (24) of the planetary row P2 is connected in parallel with the sun gear (23) of the planetary row P3, and then connected in series with the C1 clutch (1) and then connected to the input shaft (25); the sun gear (3) of the planetary row P1 is also connected in parallel with the planetary carrier (9) of the planetary row P2, and then connected in series with the C2 clutch (2), and then connected to the input shaft (25).

2. The transmission mechanism with multiple reverse gears and a step-down type as claimed in claim 1, characterized in that: The ring gear (5) of the planetary gear set P1 is also connected to a C3 brake (6).

3. The transmission mechanism with multiple reverse gears and a step-down type as claimed in claim 1, characterized in that: The ring gear (7) of the planetary gear set P2 is also connected to a C4 brake (8).

4. The transmission mechanism with multiple reverse gears and a step-down type as claimed in claim 1, characterized in that: The ring gear (11) of the planetary gear set P3 is also connected to a C5 brake (10).

5. The step-down multi-reverse transmission mechanism according to claim 1, characterized in that: The planet carrier (13) of the planetary row P4 is also connected to a C6 brake (12).

6. The transmission mechanism with multiple reverse gears and a step-down type as claimed in claim 1, characterized in that: The planet carrier (22) of the planetary gear set P3 is connected in parallel with the ring gear (14) of the planetary gear set P4 and then connected to the intermediate shaft (16) via a spline.

7. The transmission mechanism with multiple reverse gears and a step-down type as claimed in claim 1, characterized in that: The intermediate shaft (16) and the gear (17) are connected via a spline.

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