High-power planetary hydraulic transmission drive mechanism

Abstract

A high-power planetary hydraulic transmission drive mechanism, comprising: a first planetary row P1, a second planetary row P2, a third planetary row P3, a fourth planetary row P4 and a fifth planetary row P5, which are sequentially distributed in parallel. Each planetary row comprises a sun gear, a planet carrier, a planetary gear and a gear ring, wherein in the same planetary row, the planetary gear is externally meshed with the sun gear, and the planetary gear is internally meshed with the gear ring; the five sun gears are coaxial; the planet carrier of the first planetary row P1 is fixedly connected to the gear ring of the second planetary row P2; the planet carrier of the second planetary row P2 is fixedly connected to the gear ring of the third planetary row P3; the gear ring of the third planetary row P3 is fixedly connected to the planet carrier of the fourth planetary row P4; and the gear ring of the fourth planetary row P4 is fixedly connected to the sun gear of the fifth planetary row P5.

Description

A high-power planetary hydraulic transmission transmission mechanism Technical Field

[0001] The invention relates to a high-power planetary hydraulic transmission transmission mechanism, belonging to the technical field of vehicle transmission. Background Art

[0002] The planetary transmission mechanism is primarily composed of clutches, brakes, and planetary gear elements. The engagement and disengagement of different brakes or clutches allows for the coupling, decoupling, and braking of different planetary gear elements, thereby satisfying different power transmission paths and achieving outputs with varying speed ratios.

[0003] Currently, high-power planetary transmissions used in mining and construction machinery primarily utilize three or four planetary rows in parallel, resulting in a limited number of speed ratios and a narrow ratio range. With increasing international energy tensions and the deepening implementation of green development concepts, the demand for efficient and energy-efficient planetary transmissions continues to rise. The number of gears and speed ratio ranges in existing transmissions cannot maximize engine operation under economical conditions, hindering overall machine economics. Furthermore, the narrow speed ratio range places greater loads on the torque converter and transmission mechanism under the same load, making reliability difficult to guarantee.

[0004] Summary of the Invention

[0005] In order to solve the deficiencies of the prior art, the purpose of the present invention is to provide a high-power planetary hydraulic transmission transmission mechanism, which solves the problems of the prior art in that the transmission has a small number of gears and a small speed ratio range.

[0006] In order to achieve the above objectives, the present invention adopts the following technical solutions:

[0007] A high-power planetary hydraulic transmission transmission mechanism includes a first planetary row P1, a second planetary row P2, a third planetary row P3, a fourth planetary row P4, and a fifth planetary row P5, which are sequentially arranged in parallel.

[0008] The first planetary gear P1 includes a first sun gear S1, a first planet carrier PC1, a first planetary gear CA1 and a first ring gear R1. The first planetary gear CA1 is externally meshed with the first sun gear S1, and the first planetary gear CA1 is internally meshed with the first ring gear R1.

[0009] The second planetary gear P2 includes a second sun gear S2, a second planet carrier PC2, a second planetary gear CA2 and a second ring gear R2. The second planetary gear CA2 is externally meshed with the second sun gear S2, and the second planetary gear CA2 is internally meshed with the second ring gear R2.

[0010] The third planetary gear P3 includes a third sun gear S3, a third planet carrier PC3, a third planetary gear CA3 and a third ring gear R3. The third planetary gear CA3 is externally meshed with the third sun gear S3, and the third planetary gear CA3 is internally meshed with the third ring gear R3.

[0011] The fourth planetary gear P4 includes a fourth sun gear S4, a fourth planet carrier PC4, a fourth planetary gear CA4 and a fourth ring gear R4. The fourth planetary gear CA4 is externally meshed with the fourth sun gear S4, and the fourth planetary gear CA4 is internally meshed with the fourth ring gear R4.

[0012] The fifth planetary gear P5 includes a fifth sun gear S5, a fifth planet carrier PC5, a fifth planetary gear CA5, and a fifth ring gear R5. The fifth planetary gear CA5 is externally meshed with the fifth sun gear S5, and the fifth planetary gear CA5 is internally meshed with the fifth ring gear R5.

[0013] The first sun gear S1, the second sun gear S2, the third sun gear S3, the fourth sun gear S4 and the fifth sun gear S5 are arranged coaxially, the second sun gear S2 and the third sun gear S3 are fixedly connected, the first planet carrier PC1 is fixedly connected to the second ring gear R2, the second planet carrier PC2 is fixedly connected to the third ring gear R3, the third ring gear R3 is fixedly connected to the fourth planet carrier PC4, the fourth ring gear R4 is fixedly connected to the fifth sun gear S5, and the third planet carrier PC3, the fourth sun gear S4 and the fifth ring gear R5 are fixedly connected.

[0014] Furthermore, the aforementioned also includes a first clutch C1 and a second clutch C2. The inner hub body of the first clutch C1 and the outer hub body of the second clutch C2 are fixedly connected to the first sun gear S1. The outer hub body of the first clutch C1 is respectively fixedly connected to the second sun gear S2 and the third sun gear S3. The inner hub body of the second clutch C2 is fixedly connected to the second planetary carrier PC2.

[0015] Furthermore, the aforementioned also includes an input shaft In and an output shaft Out. The input shaft In and the output shaft Out are coaxially arranged. The input shaft In is respectively fixedly connected to the inner hub body of the first clutch C1, the outer hub body of the second clutch C2, and the first sun gear S1. The output shaft Out is respectively fixedly connected to the third planetary carrier PC3, the fourth sun gear S4, and the fifth ring gear R5.

[0016] Furthermore, the aforementioned also includes a first brake B1, a second brake B2, a third brake B3, a fourth brake B4, and a fifth brake B5.

[0017] The first brake B1 is used to brake the first ring gear R1 of the first planetary row P1, the second brake B2 is used to brake the second ring gear R2 of the second planetary row P2, the third brake B3 is used to brake the third ring gear R3 of the third planetary row P3, the fourth brake B4 is used to brake the fourth ring gear R4 of the fourth planetary row P4, and the fifth brake B5 is used to brake the fifth planet carrier PC5 of the fifth planetary row P5.

[0018] Furthermore, the aforementioned first clutch C1, second clutch C2, first brake B1, second brake B2, third brake B3, fourth brake B4, and fifth brake B5 are all multi-plate friction operating structures.

[0019] Furthermore, the first forward gear is achieved by simultaneously engaging the operating elements of the first clutch C1 and the fifth brake B5; the second forward gear is achieved by simultaneously engaging the operating elements of the first clutch C1 and the third brake B3; the third forward gear is achieved by simultaneously engaging the operating elements of the first clutch C1 and the fourth brake B4; the fourth forward gear is achieved by simultaneously engaging the operating elements of the first clutch C1 and the second brake B2; the fifth forward gear is achieved by simultaneously engaging the operating elements of the first clutch C1 and the first brake B1; the sixth forward gear is achieved by simultaneously engaging the operating elements of the first clutch C1 and the second clutch C2; the seventh forward gear is achieved by simultaneously engaging the operating elements of the second clutch C2 and the first brake B1; the eighth forward gear is achieved by simultaneously engaging the operating elements of the second clutch C2 and the second brake B2; the first reverse gear is achieved by simultaneously engaging the operating elements of the first brake B1 and the third brake B3; and the second reverse gear is achieved by simultaneously engaging the operating elements of the first brake B1 and the fourth brake B4.

[0020] Furthermore, the ratio of the number of teeth of the first ring gear R1 to the number of teeth of the first sun gear S1 is 1.7.

[0021] Furthermore, the ratio of the number of teeth of the second ring gear R2 to the number of teeth of the second sun gear S2 is 2.29.

[0022] Furthermore, the ratio of the number of teeth of the third ring gear R3 to the number of teeth of the third sun gear S3 is 3.7.

[0023] Furthermore, the ratio of the number of teeth of the fourth ring gear R4 to the number of teeth of the fourth sun gear S4 is 1.65.

[0024] Furthermore, the ratio of the number of teeth of the fifth ring gear R5 to the number of teeth of the fifth sun gear S5 is 1.65.

[0025] The beneficial effects achieved by the present invention are:

[0026] The system uses two clutches, five planetary gears, and five brakes to achieve eight forward gears and two reverse gears. It has a wide transmission ratio range and can better meet the needs of the entire machine for a high speed ratio, multiple gears, and a compact structure. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] FIG1 is a transmission principle diagram of the present invention.

[0028] The meaning of the reference numbers in the figure: In-input shaft; Out-output shaft; C1-first clutch; C2-second clutch; P1-first planetary gear; P2-second planetary gear; P3-third planetary gear; P4-fourth planetary gear; P5-fifth planetary gear; B1-first brake; B2-second brake; B3-third brake; B4-fourth brake; B5-fifth brake; S1-first sun gear; S2-second sun gear; S3-third sun gear; S4-fourth sun gear; S5-fifth sun gear; PC1-first planet carrier; PC2-second planet carrier; PC3-third planet carrier; PC4-fourth planet carrier; PC5-fifth planet carrier; R1-first ring gear; R2-second ring gear; R3-third ring gear; R4-fourth ring gear; R5-fifth ring gear. DETAILED DESCRIPTION

[0029] The technical solution of the present invention is described in detail below through the accompanying drawings and specific embodiments. It should be understood that the embodiments of the present application and the specific features in the embodiments are detailed descriptions of the technical solution of the present application, rather than limitations on the technical solution of the present application. Unless there is a conflict, the embodiments of the present application and the technical features in the embodiments can be combined with each other.

[0030] This embodiment discloses a high-power planetary hydraulic transmission mechanism, as shown in FIG1 , comprising an input shaft In, an output shaft Out, two clutches ( C1 , C2 ), five planetary gears ( P1 - P5 ) and five brakes ( B1 - B5 ).

[0031] Each planetary gear row includes: sun gears (S1~S5), planet carriers (PC1~PC5), planetary gears (CA1~CA5) and ring gears (R1~R5); the ring gear is coaxial with the sun gear, and the planetary gears are mounted on the planet carrier through planet shafts and bearings, and each planetary gear is internally meshed with the ring gear on the same planetary gear row and externally meshed with the sun gear on the same planetary gear row.

[0032] The five planetary gears are arranged in parallel from left to right, and the five sun gears, the input shaft In and the output shaft Out are arranged coaxially.

[0033] The input shaft In is fixedly connected to the inner hub of the first clutch C1 , the outer hub of the second clutch C2 , and the first sun gear S1 , respectively.

[0034] The outer hub body of the first clutch C1 is fixedly connected to the second sun gear S2 and the third sun gear S3 respectively.

[0035] The inner hub of the second clutch C2 is fixedly connected to the second planet carrier PC2.

[0036] The first planet carrier PC1 is fixedly connected to the second ring gear R2.

[0037] The second planet carrier PC2 is fixedly connected to the third ring gear R3.

[0038] The third ring gear R3 is fixedly connected to the fourth planet carrier PC4.

[0039] The fourth ring gear R4 is fixedly connected to the fifth sun gear S5.

[0040] The output shaft Out is fixedly connected to the third planet carrier PC3, the fourth sun gear S4, and the fifth ring gear R5 respectively.

[0041] Furthermore, the first brake B1 is used to brake the first ring gear R1 of the first planetary row P1, the second brake B2 is used to brake the second ring gear R2 of the second planetary row P2, the third brake B3 is used to brake the third ring gear R3 of the third planetary row P3, the fourth brake B4 is used to brake the fourth ring gear R4 of the fourth planetary row P4, and the fifth brake B5 is used to brake the fifth planet carrier PC5 of the fifth planetary row P5.

[0042] The transmission drive rod mechanism has five planetary gears, five brakes, and two clutches, which can achieve eight forward gears and two reverse gears.

[0043] The first clutch C1 and the second clutch C2, the first brake B1, the second brake B2, the third brake B3, the fourth brake B4, and the fifth brake B5 are all multi-plate friction control structures, using hydraulic oil to push the piston for braking. The control logic and speed ratio of each gear are shown in Table 1:

[0044] Table 1. Control logic and speed ratio of each gear (O indicates the control element is engaged)

[0045] The following describes an embodiment of the present invention in detail with reference to FIG1 and Table 1. The transmission ratio refers to the ratio of the input shaft speed to the output shaft speed.

[0046] When the operating members of the first clutch C1 and the fifth brake B5 are engaged simultaneously, the fifth planet carrier PC5 of the fifth planetary gear P5 is fixed, and the first forward gear is achieved.

[0047] When the operating members of the first clutch C1 and the third brake B3 are engaged simultaneously, the third ring gear R3 of the third planetary gear set P3 is fixed, thereby realizing the second forward gear.

[0048] When the operating members of the first clutch C1 and the fourth brake B4 are engaged simultaneously, the fourth ring gear R4 of the fourth planetary gear P4 is fixed, realizing the third forward gear.

[0049] When the operating members of the first clutch C1 and the second brake B2 are engaged simultaneously, the second ring gear R2 of the second planetary gear P2 is fixed, realizing the fourth forward gear.

[0050] When the operating elements of the first clutch C1 and the first brake B1 are engaged simultaneously, the first ring gear R1 of the first planetary gear set P1 is fixed, thereby realizing the fifth forward gear.

[0051] When the operating members of the first clutch C1 and the second clutch C2 are engaged simultaneously, the sixth forward gear can be achieved.

[0052] When the operating members of the second clutch C2 and the first brake B1 are engaged simultaneously, the first ring gear R1 of the first planetary row P1 is fixed, realizing the seventh forward gear.

[0053] When the operating members of the second clutch C2 and the second brake B2 are engaged simultaneously, the second ring gear R2 of the second planetary row P2 is fixed, realizing the eighth forward gear.

[0054] When the operating members of the first brake B1 and the third brake B3 are engaged simultaneously, the first ring gear R1 of the first planetary gear set P1 and the third ring gear R3 of the third planetary gear set P3 are fixed, respectively, to achieve one reverse gear.

[0055] When the operating members of the first brake B1 and the fourth brake B4 are engaged simultaneously, the first ring gear R1 of the first planetary gear set P1 and the fourth ring gear R4 of the fourth planetary gear set P4 are fixed, respectively, to achieve the second reverse gear.

[0056] The transmission ratios of each gear are determined by the K values ​​of the five planetary gears. This refers to the ratio of the number of teeth on the ring gear to the number of teeth on the sun gear. For example, when K1 = 1.7, K2 = 2.29, K3 = 3.7, and K4 = K5 = 1.65, the transmission ratios shown in Table 1 are obtained. This achieves a transmission mechanism with eight forward speeds and two reverse speeds. A first-gear ratio greater than 7 reduces the load on the torque converter during low-speed, heavy-load conditions in construction machinery, improving its reliability. Furthermore, the high speed ratio allows the engine to operate more efficiently, improving overall machine efficiency. As shown in Table 1, shifting between adjacent gears, whether forward or reverse, requires only one operating element, ensuring uninterrupted power, reducing frictional work and heat loss on the friction plates, and improving their reliability.

[0057] The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the technical principles of the present invention. These improvements and modifications should also be regarded as the scope of protection of the present invention.

Claims

1. A high-power planetary hydraulic transmission transmission mechanism, characterized in that: It includes a first planet row P1, a second planet row P2, a third planet row P3, a fourth planet row P4, and a fifth planet row P5 which are sequentially arranged in parallel. The first planetary row P1 includes a first sun gear S1, a first planet carrier PC1, a first planetary gear CA1 and a first ring gear R1, wherein the first planetary gear CA1 is externally meshed with the first sun gear S1, and the first planetary gear CA1 is internally meshed with the first ring gear R1; The second planetary row P2 includes a second sun gear S2, a second planet carrier PC2, a second planetary gear CA2 and a second ring gear R2, wherein the second planetary gear CA2 is externally meshed with the second sun gear S2, and the second planetary gear CA2 is internally meshed with the second ring gear R2; The third planet row P3 includes a third sun gear S3, a third planet carrier PC3, a third planet gear CA3 and a third ring gear R3. The third planet gear CA3 is externally meshed with the third sun gear S3, and the third planet gear CA3 is internally meshed with the third ring gear R3. The fourth planet row P4 includes a fourth sun gear S4, a fourth planet carrier PC4, a fourth planet gear CA4 and a fourth ring gear R4, the fourth planet gear CA4 is externally meshed with the fourth sun gear S4, and the fourth planet gear CA4 is internally meshed with the fourth ring gear R4; The fifth planet row P5 includes a fifth sun gear S5, a fifth planet carrier PC5, a fifth planet gear CA5 and a fifth ring gear R5. The fifth planet gear CA5 is externally meshed with the fifth sun gear S5, and the fifth planet gear CA5 is internally meshed with the fifth ring gear R5. The first sun gear S1, the second sun gear S2, the third sun gear S3, the fourth sun gear S4 and the fifth sun gear S5 are coaxially arranged, the second sun gear S2 and the third sun gear S3 are fixedly connected, the first planet carrier PC1 is fixedly connected to the second ring gear R2, the second planet carrier PC2 is fixedly connected to the third ring gear R3, the third ring gear R3 is fixedly connected to the fourth planet carrier PC4, the fourth ring gear R4 is fixedly connected to the fifth sun gear S5, and the third planet carrier PC3, the fourth sun gear S4 and the fifth ring gear R5 are fixedly connected.

2. A high-power planetary hydraulic transmission transmission mechanism according to claim 1, characterized in that: It also includes a first clutch C1 and a second clutch C2. The inner hub body of the first clutch C1 and the outer hub body of the second clutch C2 are fixedly connected to the first sun gear S1. The outer hub body of the first clutch C1 is fixedly connected to the second sun gear S2 and the third sun gear S3 respectively. The inner hub body of the second clutch C2 is fixedly connected to the second planetary carrier PC2.

3. A high-power planetary hydraulic transmission transmission mechanism according to claim 2, characterized in that: It also includes an input shaft In and an output shaft Out, which are coaxially arranged. The input shaft In is respectively fixedly connected to the inner hub body of the first clutch C1, the outer hub body of the second clutch C2, and the first sun gear S1, and the output shaft Out is respectively fixedly connected to the third planetary carrier PC3, the fourth sun gear S4, and the fifth ring gear R5.

4. A high-power planetary hydraulic transmission transmission mechanism according to claim 2, characterized in that: It also includes a first brake B1, a second brake B2, a third brake B3, a fourth brake B4, and a fifth brake B5. The first brake B1 is used to brake the first ring gear R1 of the first planetary row P1, the second brake B2 is used to brake the second ring gear R2 of the second planetary row P2, the third brake B3 is used to brake the third ring gear R3 of the third planetary row P3, the fourth brake B4 is used to brake the fourth ring gear R4 of the fourth planetary row P4, and the fifth brake B5 is used to brake the fifth planet carrier PC5 of the fifth planetary row P5.

5. A high-power planetary hydraulic transmission transmission mechanism according to claim 4, characterized in that: The first clutch C1, the second clutch C2, the first brake B1, the second brake B2, the third brake B3, the fourth brake B4, and the fifth brake B5 are all multi-plate friction operating structures.

6. A high-power planetary hydraulic transmission transmission mechanism according to claim 4, characterized in that: The first forward gear is realized by the simultaneous engagement of the operating members of the first clutch C1 and the fifth brake B5; the second forward gear is realized by the simultaneous engagement of the operating members of the first clutch C1 and the third brake B3; the third forward gear is realized by the simultaneous engagement of the operating members of the first clutch C1 and the fourth brake B4; the fourth forward gear is realized by the simultaneous engagement of the operating members of the first clutch C1 and the second brake B2; the fifth forward gear is realized by the simultaneous engagement of the operating members of the first clutch C1 and the first brake B1; the sixth forward gear is realized by the simultaneous engagement of the operating members of the first clutch C1 and the second clutch C2; the seventh forward gear is realized by the simultaneous engagement of the operating members of the second clutch C2 and the first brake B1; the eighth forward gear is realized by the simultaneous engagement of the operating members of the second clutch C2 and the second brake B2; the first reverse gear is realized by the simultaneous engagement of the operating members of the first brake B1 and the third brake B3; the second reverse gear is realized by the simultaneous engagement of the operating members of the first brake B1 and the fourth brake B4.

7. A high-power planetary hydraulic transmission transmission mechanism according to claim 1, characterized in that: The ratio of the number of teeth of the first ring gear R1 to the number of teeth of the first sun gear S1 is 1.

7.

8. A high-power planetary hydraulic transmission transmission mechanism according to claim 1, characterized in that: The ratio of the number of teeth of the second ring gear R2 to the number of teeth of the second sun gear S2 is 2.

29.

9. A high-power planetary hydraulic transmission transmission mechanism according to claim 1, characterized in that: The ratio of the number of teeth of the third ring gear R3 to the number of teeth of the third sun gear S3 is 3.

7.

10. A high-power planetary hydraulic transmission transmission mechanism according to claim 1, characterized in that: The ratio of the number of teeth of the fourth ring gear R4 to the number of teeth of the fourth sun gear S4 is 1.

65.

11. A high-power planetary hydraulic transmission transmission mechanism according to claim 1, characterized in that: The ratio of the number of teeth of the fifth ring gear R5 to the number of teeth of the fifth sun gear S5 is 1.65.

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