Planet wheel speed change mechanism for gearbox

Abstract

The utility model discloses a planet gear speed change mechanism for a gearbox, which belongs to the technical field of tractor transmission, and comprises a box body, a planet gear structure and a brake structure are arranged in the box body, the brake structure is meshed with the planet gear structure, one end of the inner side of the planet gear structure is connected with an input shaft group, and the other end of the inner side of the planet gear structure is connected with an output shaft group. The other end of the inner side of the planet wheel structure is connected with an output shaft, the input shaft set and the output shaft extend out of the box body in the direction away from each other, and a hydraulic oil way matched with the braking structure is arranged on the box body.

Description

Technical Field

[0001] The utility model relates to the technical field of tractor transmission, in particular to a planetary gear speed changing mechanism for a gearbox. Background Art

[0002] At present, the gear shifting mode of domestic tractor gearboxes is mostly mechanical stepped gears, and the commonly used clutch is a dry clutch. When the tractor needs to change gears, it is necessary to first step on the clutch pedal, disengage the dry clutch through the operating system, cut off the power transmitted by the engine, and then operate the shift handle to change the gear. Because the clutch operating system generally has large operating force and cumbersome operating steps, the driver's long-term frequent gear shifting increases the driver's work intensity and greatly reduces the work efficiency. Utility Model Content

[0003] In order to solve the problems existing in the prior art, the utility model provides a planetary gear speed change mechanism for a gearbox, which realizes gear shifting without stepping on the clutch through the cooperation of the hydraulic oil circuit and the braking structure, thereby increasing comfort with less cost. The planetary gear structure is cooperated with the input shaft group to complete the multi-speed power output scheme of the output shaft, and has the advantages of compact structure, large transmission ratio, and radial force balance.

[0004] In order to achieve the above purpose, the technical solution adopted by the utility model is as follows:

[0005] A planetary gear speed change mechanism for a gearbox comprises a housing, wherein a planetary gear structure and a brake structure are arranged in the housing, wherein the brake structure is meshedly connected with the planetary gear structure, an input shaft group is connected to one inner end of the planetary gear structure, and an output shaft is connected to the other inner end of the planetary gear structure, wherein the output shaft and the input shaft group extend out of the housing in a direction away from each other, and a hydraulic oil circuit matching the brake structure is arranged on the housing.

[0006] Preferably, the planetary gear structure includes a planetary carrier, one end of the planetary carrier is rotatably mounted on one end of the housing close to the input shaft group, the other end of the planetary carrier is fixedly connected to the output shaft, a plurality of evenly distributed planetary gear assemblies are rotatably mounted on the planetary carrier, a plurality of the planetary gear assemblies are meshingly connected with a first sun gear and a second sun gear parallel to each other on their inner sides, the first sun gear and the second sun gear are both fixedly mounted on the input shaft group, a first gear ring and a second gear ring are meshingly connected on their outer sides, and the outer sides of the first gear ring and the second gear ring are both arranged as circumferential gears meshingly connected to the braking structure.

[0007] Preferably, the planetary gear assembly includes a first planetary gear and a second planetary gear rotatably mounted on the planetary carrier, the first planetary gear and the second planetary gear are integrally formed and mounted on the planetary carrier, the inner and outer sides of the first planetary gear are respectively meshed with the first sun gear and the first ring gear, and the inner and outer sides of the second planetary gear are respectively meshed with the second sun gear and the second ring gear.

[0008] Preferably, the input shaft group includes a first input shaft and a second input shaft which are arranged concentrically, the second input shaft is inserted into the first input shaft, the first sun gear is fixedly mounted on the first input shaft, and the second sun gear is fixedly mounted on the second input shaft extending out of the first input shaft.

[0009] Preferably, the hydraulic oil circuit includes a left oil circuit and a right oil circuit, and the box body is provided with two annular grooves respectively connected to the left oil circuit and the right oil circuit, and the left oil circuit and the right oil circuit are respectively matched with two sides of the brake structure.

[0010] Preferably, the braking structure includes a left brake assembly and a right brake assembly, and a plurality of evenly distributed elastic reset components are installed between the left brake assembly and the right brake assembly, the outer ring of the left brake assembly is meshingly connected with the first gear ring, and the outer ring of the right brake assembly is meshingly connected with the second gear ring, and piston rings corresponding to the left brake assembly and the right brake assembly are respectively installed in the two ring grooves.

[0011] The beneficial effects of the utility model are shown in

[0012] 1. In the utility model, the gear shifting is realized without stepping on the clutch by cooperating with the hydraulic oil circuit and the brake structure, thereby increasing the comfort with less cost;

[0013] 2. The utility model adopts a planetary gear structure and an input shaft group to cooperate with each other to complete the multi-speed power output scheme of the output shaft, which has the advantages of compact structure, large transmission ratio, and radial force balance;

[0014] 3. In the utility model, the first planetary gear and the second planetary gear are designed as an integral part, and with the brake structure, it is possible to control the rotation speed of the two ring gears by one sun gear, and to fix the first planetary gear and the second planetary gear by rotating the two sun gears at the same time, which can effectively increase the output speed of the output shaft. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 It is a sectional view of the overall structure of the planetary gear speed change mechanism for the gearbox of the utility model.

[0016] In the figure: 1-housing, 2-output shaft, 3-planet carrier, 4-first sun gear, 5-second sun gear, 6-first ring gear, 7-second ring gear, 8-first planetary gear, 9-second planetary gear, 10-second input shaft, 11-first input shaft, 12-left oil circuit, 13-right oil circuit, 14-ring groove, 15-left brake assembly, 16-right brake assembly, 17-piston ring. DETAILED DESCRIPTION

[0017] In order to facilitate understanding by those skilled in the art, the present invention is further described below in conjunction with the accompanying drawings.

[0018] like Figure 1 A planetary gear speed change mechanism for a gearbox shown in the figure comprises a case 1, wherein a planetary gear structure and a brake structure are arranged in the case 1, wherein the brake structure is meshedly connected with the planetary gear structure, an input shaft group is connected to one end of the inner side of the planetary gear structure, and an output shaft 2 is connected to the other end of the inner side of the planetary gear structure, wherein the output shaft and the input shaft group 2 extend out of the case 1 in directions away from each other, and neither the output shaft nor the input shaft group 2 is in contact with the case 1, and a hydraulic oil circuit matched with the brake structure is arranged on the case 1, wherein gear shifting is achieved without stepping on a clutch through the coordination of the hydraulic oil circuit and the brake structure, thereby obtaining greater comfort with less cost, and a multi-speed power output scheme of the output shaft 2 is completed by coordination of the planetary gear structure and the input shaft group, and has the advantages of compact structure, large transmission ratio, and radial force balance, etc.

[0019] The planetary gear structure includes a planetary carrier 3, a bearing is provided between one end of the planetary carrier 3 close to the input shaft group and the housing to realize rotational connection, the other end of the planetary carrier 3 is fixedly mounted on the output shaft 2, the end of the output shaft 2 away from the input shaft group extends out of the housing, a bearing is also provided between the output shaft and the housing to realize rotational connection, a number of evenly distributed planetary gear assemblies are rotatably mounted on the planetary carrier 3, a first sun gear 4 and a second sun gear 5 parallel to each other are meshed and connected on the inner sides of a number of the planetary gear assemblies, the second sun gear 5 is located on the side of the first sun gear 4 close to the output shaft 2, one end of the input shaft group is inserted in the planetary carrier and is fixedly connected to the first sun gear 4 and the second sun gear 5, the planetary The outer side of the wheel assembly is meshed with a first ring gear 6 and a second ring gear 7, and the outer sides of the first ring gear 6 and the second ring gear 7 are both set as circumferential gears meshed with the braking structure; the planetary gear assembly includes a first planetary gear 8 and a second planetary gear 9 rotatably mounted on the planetary carrier 3, the first planetary gear 8 and the first planetary gear 8 are integrally mounted on the planetary carrier 3, the inner and outer sides of the first planetary gear 8 are respectively meshed with the first sun gear 4 and the first ring gear 6, the inner and outer sides of the second planetary gear 9 are respectively meshed with the second sun gear 5 and the second ring gear 7, and the first ring gear 6 and the second ring gear 7 can both rotate around the axis of the planetary carrier 3; by utilizing the different gear ratios between different gear meshing, the speed of the output shaft 2 can be adjusted to achieve multi-speed power output.

[0020] The input shaft group includes a first input shaft 11 and a second input shaft 10 which are arranged concentrically. The second input shaft 10 is inserted into the first input shaft 11. A gap is provided between the first input shaft 11 and the second input shaft 10. The existence of the gap enables the first input shaft 11 and the second input shaft 10 to rotate independently. Both ends of the second output shaft 10 extend out of the two ends of the first input shaft 11 respectively. One end of the first input shaft 11 extends into the planetary carrier and is fixedly connected to the first sun gear 4. One end of the second input shaft 10 extends out of the first input shaft 11 and is fixedly connected to the second sun gear 5.

[0021] The hydraulic oil circuit includes a left oil circuit 12 and a right oil circuit 13. The box body 1 is provided with two annular grooves 14 respectively connected with the left oil circuit 12 and the right oil circuit 13. The left oil circuit 12 and the right oil circuit 13 are respectively matched with the two sides of the brake structure; the brake structure includes a left brake assembly 15 and a right brake assembly 16. A number of evenly distributed elastic reset components are installed between the left brake assembly 15 and the right brake assembly 16. The outer ring of the left brake assembly 15 is meshed and connected with the first gear ring 6, and the outer ring of the right brake assembly 16 is meshed and connected with the second gear ring 7. Piston rings 17 corresponding to the left brake assembly 15 and the right brake assembly 16 are respectively installed in the two annular grooves 14. One or two of the two piston rings 17 are pushed by hydraulic oil, and the corresponding left brake assembly 15 or right brake assembly 16 is squeezed by the piston ring 17 to achieve braking of the first gear ring 6 or the second gear ring 7.

[0022] The working principle of the utility model is as follows:

[0023] When the first input shaft 11 rotates, the corresponding piston ring 17 is pushed by the left oil passage 12 to drive the right brake assembly 16 to fix the first gear ring 6, the first input shaft 11 drives the first sun gear 4 to rotate, the rotation of the first sun gear 4 drives the first planetary gear 8 and the second planetary gear 9 which are integrally arranged to rotate, the second planetary gear 9 drives the second gear ring 7 to rotate, the first gear ring 6 is fixed to achieve the first planetary gear 8 to perform a circular motion around the first gear ring 6, and then drives the planet carrier 3 to rotate, and the planet carrier 3 drives the output shaft 2 to output power at speed 1;

[0024] When the first input shaft 11 rotates, the corresponding piston ring 17 is pushed through the right oil passage 13 to drive the left brake assembly 15 to fix the second gear ring 7, the first input shaft 11 drives the first sun gear 4 to rotate, the rotation of the first sun gear 4 drives the first planetary gear 8 and the second planetary gear 9 which are integrally arranged to rotate, the first planetary gear 8 drives the first gear ring 6 to rotate, the second gear ring 7 is fixed to realize the second planetary gear 9 to perform a circular motion around the second gear ring 7, and then drives the planet carrier 3 to rotate, and the planet carrier 3 drives the output shaft 2 to output power at speed 2;

[0025] When the second input shaft 10 rotates, the corresponding piston ring 17 is pushed by the left oil passage 12 to drive the right brake assembly 16 to fix the first ring gear 6, the second input shaft 10 drives the second sun gear 5 to rotate, the rotation of the second sun gear 5 drives the second planetary gear 9 and the first planetary gear 8 which are integrally arranged to rotate, the second planetary gear 9 drives the second ring gear 7 to rotate, the first ring gear 6 is fixed to achieve the first planetary gear 8 to perform a circular motion around the first ring gear 6, and then drives the planet carrier 3 to rotate, and the planet carrier 3 drives the output shaft 2 to output power at speed three;

[0026] When the second input shaft 10 rotates, the corresponding piston ring 17 is pushed through the right oil passage 13 to drive the left brake assembly 15 to fix the second ring gear 7, the second input shaft 10 drives the second sun gear 5 to rotate, the rotation of the second sun gear 5 drives the first planetary gear 8 and the second planetary gear 9 which are integrally arranged to rotate, the first planetary gear 8 drives the first ring gear 6 to rotate, the second ring gear 7 is fixed to realize the second planetary gear 9 to perform a circular motion around the second ring gear 7, and then drives the planet carrier 3 to rotate, and the planet carrier 3 drives the output shaft 2 to output power at speed four;

[0027] When the first input shaft 11 and the second input shaft 10 rotate at the same speed, the first input shaft 11 drives the first sun gear 4 to rotate, and the second input shaft 10 drives the second sun gear 5 to rotate. Since the gear ratio between the first sun gear 4 and the first planetary gear 8 is different from the gear ratio between the second sun gear 5 and the second planetary gear 9, the first planetary gear 8 and the second planetary gear 9 which are integrally arranged are fixed, so the first input shaft and the second input shaft with the same speed directly drive the planetary carrier 3 to rotate, and the planetary carrier 3 drives the output shaft 2 to output power at speed 5.

[0028] Speed ​​1, speed 2, speed 3, speed 4 and speed 5 in the above process are five different output speeds obtained by the output shaft 2 according to different gear ratios in the planetary gear structure when the rotation speeds of the first input shaft 11 and the second input shaft 10 are determined.

[0029] The above contents are merely examples and explanations of the structure of the utility model. The technicians in this technical field may make various modifications or additions to the specific embodiments described or replace them in a similar manner. As long as they do not deviate from the structure of the utility model or exceed the scope defined in the claims, they should all fall within the protection scope of the utility model.

Claims

1. A planetary gear transmission mechanism for a gearbox, characterized in that: It includes a box body, in which a planetary gear structure and a brake structure are arranged, the brake structure is meshedly connected with the planetary gear structure, one end of the inner side of the planetary gear structure is connected to an input shaft group, and the other end of the inner side of the planetary gear structure is connected to an output shaft, the output shaft and the input shaft group extend out of the box body in a direction away from each other, and the box body is provided with a hydraulic oil circuit that matches the brake structure.

2. A planetary gear speed change mechanism for a gearbox according to claim 1, characterized in that: The planetary gear structure includes a planetary carrier, one end of which is rotatably mounted on the housing close to the input shaft group, and the other end of the planetary carrier is fixedly connected to the output shaft. A number of evenly distributed planetary gear assemblies are rotatably mounted on the planetary carrier, and a first sun gear and a second sun gear parallel to each other are meshedly connected on the inner sides of the number of planetary gear assemblies, and the first sun gear and the second sun gear are both fixedly mounted on the input shaft group, and a first gear ring and a second gear ring are meshedly connected on the outer sides of the planetary gear assemblies, and the outer sides of the first gear ring and the second gear ring are both set as circumferential gears meshedly connected to the braking structure.

3. A planetary gear speed change mechanism for a gearbox according to claim 2, characterized in that: The planetary gear assembly includes a first planetary gear and a second planetary gear rotatably mounted on the planetary carrier. The first planetary gear and the second planetary gear are integrally formed and mounted on the planetary carrier. The inner and outer sides of the first planetary gear are respectively meshed with the first sun gear and the first ring gear, and the inner and outer sides of the second planetary gear are respectively meshed with the second sun gear and the second ring gear.

4. A planetary gear speed change mechanism for a gearbox according to claim 3, characterized in that: The input shaft group includes a first input shaft and a second input shaft which are arranged concentrically. The second input shaft is inserted into the first input shaft. The first sun gear is fixedly mounted on the first input shaft. The second sun gear is fixedly mounted on the second input shaft extending out of the first input shaft.

5. The planetary gear speed change mechanism for a gearbox according to claim 2, characterized in that: The hydraulic oil circuit includes a left oil circuit and a right oil circuit. The box body is provided with two annular grooves respectively connected with the left oil circuit and the right oil circuit. The left oil circuit and the right oil circuit are respectively matched with two sides of the brake structure.

6. A planetary gear speed change mechanism for a gearbox according to claim 5, characterized in that: The braking structure includes a left brake assembly and a right brake assembly, and a plurality of evenly distributed elastic reset components are installed between the left brake assembly and the right brake assembly. The outer ring of the left brake assembly is meshed and connected with the first gear ring, and the outer ring of the right brake assembly is meshed and connected with the second gear ring. Piston rings corresponding to the left brake assembly and the right brake assembly are respectively installed in the two ring grooves.

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