CN108533701B - Multi-section multi-clutch type hydraulic mechanical continuously variable transmission with double planet rows - Google Patents

Multi-section multi-clutch type hydraulic mechanical continuously variable transmission with double planet rows Download PDF

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Publication number
CN108533701B
CN108533701B CN201810306712.4A CN201810306712A CN108533701B CN 108533701 B CN108533701 B CN 108533701B CN 201810306712 A CN201810306712 A CN 201810306712A CN 108533701 B CN108533701 B CN 108533701B
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CN
China
Prior art keywords
gear
clutch
shaft
hydraulic motor
hollow shaft
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Expired - Fee Related
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CN201810306712.4A
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Chinese (zh)
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CN108533701A (en
Inventor
曹付义
李豪迪
邓瑞涛
张风丽
王浩然
马可
李金龙
崔梦凯
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Luoyang High Tech Development Zone Zhongcheng Electronic Firm
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Henan University of Science and Technology
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Priority to CN201810306712.4A priority Critical patent/CN108533701B/en
Publication of CN108533701A publication Critical patent/CN108533701A/en
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Expired - Fee Related legal-status Critical Current
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0078—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratio comprising twelve or more forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds

Abstract

The invention relates to the field of transmission equipment of engineering vehicles, in particular to a double-planet-row multi-section multi-clutch type hydraulic mechanical continuously variable transmission. The hydraulic transmission device comprises a hydraulic transmission assembly, a mechanical transmission assembly, an input shaft and an output shaft which are arranged in parallel; on the premise of meeting more modes, the multi-mode switching control device is simpler and more compact in structure, can adopt electromagnetic proportional hydraulic control, enables multi-working-condition multi-mode switching control to be more flexible, guarantees that the speed of the vehicle is switched steadily at different stages, reduces impact, and improves the dynamic property of the vehicle.

Description

Multi-section multi-clutch type hydraulic mechanical continuously variable transmission with double planet rows
Technical Field
The invention relates to the field of transmission equipment of engineering vehicles, in particular to a double-planet-row multi-section multi-clutch type hydraulic mechanical continuously variable transmission.
Background
The high-power heavy vehicle has complex working conditions and frequent fluctuation of external load, and requires the transmission to change the rotating speed and the torque timely to adapt to the continuous change of the actual load, thereby ensuring the dynamic property and the fuel economy of the vehicle. Although the stepped transmission box in the prior art can meet certain requirements through gear shifting, the stepped transmission box can only transmit power according to a fixed transmission ratio, continuous speed change cannot be realized, if gears are increased, the complexity of the mechanical structure of the transmission is increased, the cost is increased, the operation is difficult, and the improvement of the performance of the stepped transmission box is severely limited.
Disclosure of Invention
The invention aims to provide a double-planet-row multi-section multi-clutch type hydraulic mechanical stepless speed changer which not only can realize multi-section large-range stepless speed regulation performance, but also can meet the multi-mode requirement of a vehicle running under different working conditions.
In order to solve the technical problems, the invention adopts the technical scheme that: a double-planet-row multi-section multi-clutch type hydraulic mechanical stepless speed changer comprises a hydraulic transmission assembly, a mechanical transmission assembly, an input shaft and an output shaft which are arranged in parallel; the hydraulic transmission assembly comprises a variable displacement hydraulic pump and a quantitative hydraulic motor which are arranged in series, a hydraulic motor shaft is arranged at the output end of the quantitative hydraulic motor, and the hydraulic motor shaft is arranged in parallel to the input shaft and the output shaft; the mechanical transmission assembly comprises a front planet row confluence device, a rear planet row confluence device, a fixed-axis gear pair and a section changing device, wherein the front planet row confluence device comprises a front sun gear fixedly arranged on a hydraulic motor shaft, a front gear ring rotatably arranged on the hydraulic motor shaft, a plurality of front planet gears arranged between the front sun gear and the front gear ring in a matched mode and a front planet carrier rotatably arranged on the hydraulic motor shaft and matched with the front planet gears, the rear planet row confluence device comprises a rear sun gear fixedly arranged on the hydraulic motor shaft, a rear gear ring rotatably arranged on the hydraulic motor shaft, a plurality of rear planet gears arranged between the rear sun gear and the rear gear ring in a matched mode and a rear planet carrier rotatably arranged on the hydraulic motor shaft and matched with the rear planet gears, the fixed-axis gear pair comprises a second gear rotatably arranged on the hydraulic motor shaft and fixedly connected with the front planet carrier and a first gear, a third gear, a fourth gear and a section changing device, the front planet gear and the front, A fifth gear which is rotationally arranged on the hydraulic motor shaft and is fixedly connected with the front gear ring, a fourth gear and a sixth gear which are respectively in meshed connection with the fifth gear, a seventh gear which is fixedly arranged on the input shaft, a hydraulic pump gear and an idle gear which are respectively in meshed connection with the seventh gear, a tenth gear which is rotationally arranged on the hydraulic motor shaft and is fixedly connected with the rear gear ring, a ninth gear and an eleventh gear which are respectively in meshed connection with the tenth gear, a thirteenth gear which is rotationally arranged on the hydraulic motor shaft and is fixedly connected with the rear planet carrier, and a twelfth gear and a fourteenth gear which are respectively in meshed connection with the thirteenth gear, wherein the first gear, the fourth gear, the ninth gear and the twelfth gear are respectively rotationally arranged on the input shaft, and the third gear, the sixth gear, the eleventh gear and the fourteenth gear are respectively rotationally arranged on the output shaft, the hydraulic pump gear is fixedly arranged at the input end of the variable displacement hydraulic pump, the segment changing device comprises a first synchronizer for controlling the first gear and the fourth gear to be respectively clutched with the input shaft, a second synchronizer for controlling the ninth gear and the twelfth gear to be respectively clutched with the input shaft, a third synchronizer for controlling the third gear and the sixth gear to be respectively clutched with the output shaft, a fourth synchronizer for controlling the eleventh gear and the fourteenth gear to be respectively clutched with the output shaft and a clutch assembly, the clutch assembly comprises a shell rotationally arranged on the hydraulic motor shaft, a front gear ring clutch for controlling the front gear ring to be clutched with the shell, a front planet carrier clutch for controlling the front planet carrier to be clutched with the shell, a rear planet carrier clutch for controlling the rear planet carrier to be clutched with the shell and a rear gear ring clutch for controlling the rear gear ring to be clutched with the shell, an eighth gear is fixedly arranged on the shell and is in transmission connection with the idle gear.
Preferably, one end of the input shaft, which is close to the front planet row confluence device, is used for being connected with the engine, and one end of the input shaft, which is close to the rear planet row confluence device, is used for being connected with the power output device.
Preferably, a first hollow shaft and a second hollow shaft are rotatably arranged on the hydraulic motor shaft, a third hollow shaft is rotatably arranged on the periphery of the first hollow shaft, a fourth hollow shaft is rotatably arranged on the periphery of the second hollow shaft, one end of the first hollow shaft is fixedly connected with the second gear, the middle part of the first hollow shaft is fixedly connected with the front planet carrier, the other end of the first hollow shaft is connected with the front planet carrier clutch, one end of the second hollow shaft is fixedly connected with the thirteenth gear, the middle part of the second hollow shaft is fixedly connected with the rear planet carrier, the other end of the second hollow shaft is connected with the rear planet carrier clutch, one end of the third hollow shaft is fixedly connected with the fifth gear, the middle part of the third hollow shaft is fixedly connected with the front gear ring, the other end of the third hollow shaft is connected with the front gear ring clutch, and one end of the fourth hollow shaft is fixedly connected with the tenth gear, the middle part of the fourth hollow shaft is fixedly connected with the rear gear ring, and the other end of the fourth hollow shaft is connected with the rear gear ring clutch.
Advantageous effects
When the double-planet-row multi-section multi-clutch type hydraulic mechanical stepless speed changer works, the front planet-row confluence device, the rear planet-row confluence device, the fixed-shaft gear pair and the segment-changing device are used as a mechanical transmission path, the variable-displacement hydraulic pump and the quantitative hydraulic motor which are connected in series are used as a hydraulic transmission path, and the transmission conversion under different modes of a pure mechanical mode, a moment-dividing speed-converging type hydraulic mechanical hybrid power mode and a pure hydraulic pressure is realized through the logical control of each clutch and synchronizer in the segment-changing device by a hydraulic system, so that the speed change range is improved, the multi-gear stepless speed regulation performance requirement of a high-power vehicle is met to a great extent, and the adaptability of the high-power vehicle under various working conditions such as high-load low-speed operation, traction transportation, low-load transition and the like. The pure mechanical mode has high transmission efficiency and can be used for long-distance high-speed transition driving; the hydraulic mechanical hybrid power mode can realize stepless speed regulation performance on the basis of mechanical transmission, has strong adaptability and is suitable for most working condition requirements; although the transmission efficiency of the pure hydraulic mode is lower than that of the hydraulic mechanical hybrid power mode, the engine can be always operated in a high-efficiency region, the output torque and the rotating speed are not influenced by the input torque and the rotating speed, and the power requirement of a vehicle under a large load and a low speed can be met.
The double-planet-row multi-section multi-clutch type hydraulic mechanical stepless transmission has the advantages that the structure is simpler and more compact on the premise of meeting more modes, electromagnetic proportional hydraulic control can be adopted, multi-working-condition multi-mode switching control is more flexible, the speed switching stability of a vehicle at different stages is ensured, the impact is reduced, and the dynamic property of the vehicle is improved.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic diagram of a pure mechanical gear transmission form M1 gear of the present invention;
FIG. 3 is a schematic diagram of a hydromechanical hybrid transmission form HM1 gear of the front planetary bus conflux of the present invention;
FIG. 4 is a schematic diagram of a hydromechanical hybrid transmission form HM5 ratio of the present invention where the front planetary bar confluence passes through the rear planetary bar output;
FIG. 5 is a schematic diagram of the pure hydrostatic transmission form H1 gear output by the front planetary row of the present invention;
FIG. 6 is a schematic representation of the hydromechanical hybrid reverse version of the present invention gear R1 output in the front planetary row;
FIG. 7 is a control diagram of clutch logic for each gear of the present invention;
the labels in the figure are: 1. second gear, 2, first gear, 3, first synchronizer, 4, fourth gear, 5, fifth gear, 6, variable displacement hydraulic pump, 7, hydraulic pump gear, 8, seventh gear, 9, idler, 10, eighth gear, 11, rear ring gear, 12, ninth gear, 13, second synchronizer, 14, twelfth gear, 15, input shaft, 16, rear planet gear, 17, rear planet carrier, 18, rear sun gear, 19, hydraulic motor shaft, 20, tenth gear, 21, thirteenth gear, 22, output shaft, 23, fourteenth gear, 24, fourth synchronizer, 25, eleventh gear, 26, rear ring gear clutch, 27, rear planet carrier clutch, 28, forward planet carrier clutch, 29, forward ring gear clutch, 30, forward ring gear, 31, sixth gear, 32, third synchronizer, 33, third gear, 34, forward planet gear, 35, forward planet carrier, 36. Front sun gear, 37, fixed displacement hydraulic motor, M, pure mechanical gear, HM, hydro-mechanical hybrid gear, H, pure hydraulic gear, R, hydro-mechanical hybrid reverse gear, ●, engaged state.
Detailed Description
As shown in fig. 1, the double-planet-row multistage multi-clutch type hydraulic mechanical continuously variable transmission of the present invention comprises a casing, a hydraulic transmission assembly and a mechanical transmission assembly which are arranged in the casing, and an input shaft 15 and an output shaft 22 which are arranged in parallel. The two ends of the input shaft 15 and the output shaft 22 are rotatably arranged on the side wall of the casing and are positioned outside the inner cavity of the casing through bearings respectively. The left end of the input shaft 15 is shown for driving connection to the engine and the right end is shown for connection to the power take-off PTO, so that part of the power from the engine is supplied to other mechanisms provided on the vehicle. The traveling power is supplied to the traveling wheels of the vehicle through the right end of the output shaft 22.
The hydraulic transmission assembly comprises a variable displacement hydraulic pump 6 and a fixed displacement hydraulic motor 37 which are arranged in series, wherein a hydraulic motor shaft 19 is arranged at the output end of the fixed displacement hydraulic motor 37, and the hydraulic motor shaft 19 is arranged in parallel with the input shaft 15 and the output shaft 22.
The mechanical transmission assembly comprises a front planet row collecting device, a rear planet row collecting device, a fixed-axis gear pair and a section changing device, wherein the front planet row collecting device comprises a front sun gear 36 fixedly arranged on a hydraulic motor shaft 19, a front gear ring 30 rotatably arranged on the hydraulic motor shaft 19, a plurality of front planet gears 34 arranged between the front sun gear 36 and the front gear ring 30 in a matched mode, and a front planet carrier 35 rotatably arranged on the hydraulic motor shaft 19 and matched with the plurality of front planet gears 34, the rear planet row collecting device comprises a rear sun gear 18 fixedly arranged on the hydraulic motor shaft 19, a rear gear ring 11 rotatably arranged on the hydraulic motor shaft 19, a plurality of rear planet gears 16 arranged between the rear sun gear 18 and the rear gear ring 11 in a matched mode, and a rear planet carrier 17 rotatably arranged on the hydraulic motor shaft 19 and matched with the plurality of rear planet gears 16.
The fixed-axis gear pair comprises a second gear 1 which is rotatably arranged on the hydraulic motor shaft 19 and is fixedly connected with a front planet carrier 35, a first gear 2 and a third gear 33 which are respectively meshed with the second gear 1, a fifth gear 5 which is rotatably arranged on the hydraulic motor shaft 19 and is fixedly connected with a front ring gear 30, a fourth gear 4 and a sixth gear 31 which are respectively meshed with the fifth gear 5, a seventh gear 8 which is fixedly arranged on the input shaft 15, a hydraulic pump gear 7 and an idle gear 9 which are respectively meshed with the seventh gear 8, a tenth gear 20 which is rotatably arranged on the hydraulic motor shaft 19 and is fixedly connected with a rear ring gear 11, a ninth gear 12 and an eleventh gear 25 which are respectively meshed with the tenth gear 20, a thirteenth gear 21 which is rotatably arranged on the hydraulic motor shaft 19 and is fixedly connected with a rear planet carrier 17, and a twelfth gear 14 and a fourteenth gear 23 which are respectively meshed with the thirteenth gear 21, the first gear 2, the fourth gear 4, the ninth gear 12 and the twelfth gear 14 are respectively and rotatably arranged on the input shaft 15, the third gear 33, the sixth gear 31, the eleventh gear 25 and the fourteenth gear 23 are respectively and rotatably arranged on the output shaft 22, and the hydraulic pump gear 7 is fixedly arranged at the input end of the variable displacement hydraulic pump 6.
The segment changing device comprises a first synchronizer 3 for controlling the clutching between the first gear 2 and the fourth gear 4 and the input shaft 15 respectively, a second synchronizer 13 for controlling the clutching between the ninth gear 12 and the twelfth gear 14 and the input shaft 15 respectively, a third synchronizer 32 for controlling the clutching between the third gear 33 and the sixth gear 31 and the output shaft 22 respectively, a fourth synchronizer 24 for controlling the clutching between the eleventh gear 25 and the fourteenth gear 23 and the output shaft 22 respectively, and a clutch assembly, wherein the clutch assembly comprises a shell rotationally arranged on a hydraulic motor shaft 19, a front ring gear clutch 29 for controlling the clutching between a front ring gear 30 and the shell, a front planet carrier clutch 28 for controlling the clutching between a front planet carrier 35 and the shell, a rear planet carrier clutch 27 for controlling the clutching between a rear planet carrier 17 and the shell, and a rear ring gear clutch 26 for controlling the clutching between a rear ring gear 11 and the shell, an eighth gear 10 is fixedly arranged on the shell, and the eighth gear 10 is in transmission connection with the idle wheel 9.
The first synchronizer 3 in the embodiment is arranged on the input shaft 15 between the first gear 2 and the fourth gear 4, the second synchronizer 13 is arranged on the input shaft 15 between the ninth gear 12 and the twelfth gear 14, the third synchronizer 32 is arranged on the output shaft 22 between the third gear 33 and the sixth gear 31, the fourth synchronizer 24 is arranged on the output shaft 22 between the eleventh gear 25 and the fourteenth gear 23, and the engagement or the disengagement between the gears at the two sides of the synchronizer and the corresponding shafts is controlled by one synchronizer. In fig. 7, each synchronizer of the synchronizer sections has two modes, i.e., 3 in the M1 has "●" marked on the left, i.e., it means that the first synchronizer 3 engages the first gear 2 on the left side thereof with the corresponding input shaft 15, 3 has no mark on the right, i.e., it means that the first synchronizer 3 does not engage the fourth gear 4 on the right side thereof with the input shaft 15, the fourth gear 4 can still rotate relative to the input shaft 15, and so on.
A first hollow shaft and a second hollow shaft are rotatably arranged on the hydraulic motor shaft 19, a third hollow shaft is rotatably arranged on the periphery of the first hollow shaft, and a fourth hollow shaft is rotatably arranged on the periphery of the second hollow shaft. One end of the first hollow shaft is fixedly connected with the second gear 1, the middle part of the first hollow shaft is fixedly connected with the front planet carrier 35, the other end of the first hollow shaft is connected with the front planet carrier clutch 28, one end of the second hollow shaft is fixedly connected with the thirteenth gear 21, the middle part of the second hollow shaft is fixedly connected with the rear planet carrier 17, the other end of the second hollow shaft is connected with the rear planet carrier clutch 27, one end of the third hollow shaft is fixedly connected with the fifth gear 5, the middle part of the third hollow shaft is fixedly connected with the front gear ring 30, the other end of the third hollow shaft is connected with the front gear ring clutch 29, one end of the fourth hollow shaft is fixedly connected with the tenth gear 20, the middle part of the fourth hollow shaft is fixedly connected with the rear gear ring 11, and the other end of the fourth hollow shaft is connected with the rear gear ring clutch.
The power transmission and gear shifting of the pure mechanical section, the forward gear of the hydro-mechanical mixing section, the pure hydraulic section and the reverse gear of the hydro-mechanical mixing section of the double-planet-row multi-section multi-clutch type hydro-mechanical continuously variable transmission are further described by 5 specific embodiments.
Embodiment 1, a pure mechanical transmission form M1 gear of a double-planet row multistage multi-clutch type hydraulic mechanical continuously variable transmission: as shown in fig. 2, power transmitted from the engine passes through the first synchronizer 3, the first synchronizer 3 is engaged with the first gear 2, and one power is transmitted to the power output apparatus through the input shaft 15; the other path of power passes through the first gear 2, the second gear 1 and the third gear 33, at this time, the third synchronizer 32 is engaged with the third gear 33, the clutch assembly is in a separated state, the front gear ring 30 is in an unconstrained state, and the power is transmitted to the output shaft 22 through the third synchronizer 32 and finally output to the vehicle running device.
Similar to the M1 gear in the pure mechanical transmission mode, the M2 gear, the M3 gear and the M4 gear are also arranged, and detailed description is omitted. The invention has 4 pure mechanical gears.
Embodiment 2, a hydraulic mechanical hybrid transmission mode HM1 gear of a double-planet-row multi-segment multi-clutch type hydraulic mechanical stepless transmission with front planet-row confluence output: as shown in fig. 3, the power transmitted from the engine passes through the first synchronizer 3, the first synchronizer 3 is engaged with the first gear 2, one path of power is transmitted to the hydraulic transmission assembly and the power output device through the input shaft 15 and the seventh gear 8, and the power passing through the hydraulic transmission assembly is finally transmitted to the front sun gear 36 of the front planetary gear confluence device; the other path of power is transmitted to the front planet carrier 35 through the first gear 2 and the second gear 1. The two paths of power flows are converged at the front planet row converging device and are output to the fifth gear 5 and the sixth gear 31 by the front gear ring 30, at the moment, the third synchronizer 32 is connected with the sixth gear 31, the clutch assembly is in a separated state, and the power is transmitted to the output shaft 22 through the third synchronizer 32 and is finally output to the vehicle running device.
Similar to the HM1 gear, which is the hydromechanical hybrid transmission form of the front planetary output, there is also HM2 gear; likewise, the hydraulic mechanical hybrid transmission forms of the rear planet bar confluence output include an HM3 gear and an HM4 gear, which are not described in detail herein. The invention has 4 hydraulic mechanical hybrid transmission forms with planet bar confluence output.
Embodiment 3, a double-planet-row multistage multi-clutch type hydromechanical continuously variable transmission is characterized in that the confluence of a front planet row passes through a hydromechanical hybrid transmission mode HM5 gear output by a rear planet row: as shown in fig. 4, the power transmitted from the engine passes through the first synchronizer 3, the first synchronizer 3 is engaged with the first gear 2, one path of power is transmitted to the hydraulic transmission assembly and the power output device through the input shaft 15 and the seventh gear 8, and the power passing through the hydraulic transmission assembly is finally transmitted to the front sun gear 36 of the front planetary gear confluence device; the other path of power is transmitted to the front planet carrier 35 through the first gear 2 and the second gear 1. The two paths of power flows are converged at the front planetary row converging device and output to the clutch assembly through the front gear ring 30, at the moment, the front gear ring clutch 29 and the rear planet carrier clutch 27 are connected, the power is transmitted to the rear planet carrier 17, the thirteenth gear 21 and the fourteenth gear 23 through the clutch assembly, the fourth synchronizer 24 is connected with the fourteenth gear 23, and the power is transmitted to the output shaft 22 through the fourth synchronizer 24 and finally output to the vehicle running device.
Similar to the HM5 gear of the hydraulic mechanical hybrid transmission form output by the front planet row after passing through the rear planet row, the hydraulic mechanical hybrid transmission form also comprises HM6 gear, HM7 gear and HM8 gear; likewise, the rear planet bar confluence is in the form of a hydraulic mechanical hybrid transmission with the output of the front planet bar, such as an HM9 gear, an HM10 gear, an HM11 gear and an HM12 gear, which are not described in detail herein. The invention has 8 hydraulic-mechanical hybrid transmission forms which are output from the planetary row through another planetary row.
Embodiment 4, a pure hydraulic transmission type H1 gear of a double-planetary-row multi-stage multi-clutch type hydromechanical continuously variable transmission output by a front planetary row: as shown in fig. 5, the power transmitted from the engine is transmitted to the hydraulic transmission assembly and the power output device through the input shaft 15 and the seventh gear 8, the power passing through the hydraulic transmission assembly is finally transmitted to the front sun gear 36 of the front planetary row, and at the same time, the front ring gear clutch 29 and the front carrier clutch 28 are engaged, and at this time, the front planetary row is in a single-input single-output state, the power is output by the front ring gear 30, the power is transmitted to the output shaft 22 through the third synchronizer 32, and finally output to the vehicle running device, through the fifth gear 5 and the sixth gear 31, and the third synchronizer 32 is engaged with the sixth gear 31.
Also similar to the pure hydrostatic version of the front planetary row output, gear H1, is gear H2; the pure hydraulic transmission forms H3 and H4, which are also output from the rear planetary row, are not described in detail here. The invention has 4 pure hydraulic transmission forms.
Embodiment 5, a hydro-mechanical hybrid reverse gear transmission form R1 gear of a double-planet-row multi-stage multi-clutch hydro-mechanical continuously variable transmission output by a front planet row: as shown in fig. 6, the power transmitted from the engine is divided into three paths of power through the input shaft 15 and the seventh gear 8, the first path is transmitted to the hydraulic transmission assembly, the second path is transmitted to the idle gear 9, and the third path is transmitted to the power output device; the power flowing through the hydraulic transmission assembly is finally transmitted to a front sun gear 36 of a front planet row confluence device, the power flowing through an idle gear 9 is transmitted to a clutch assembly through an eighth gear 10, at the moment, a front planet carrier clutch 28 is engaged, the power is transmitted to a front planet carrier 35, confluence of two paths of power is realized at a front planet row, the power is output by a front gear ring 30, the power passes through a fifth gear 5 and a sixth gear 31, a third synchronizer 32 is engaged with the sixth gear 31, the power is transmitted to an output shaft 22 through the third synchronizer 32, and finally the power is output to a vehicle running device.
Similar to the hydro-mechanical hybrid reverse drive type R1 gear output by the front planetary row, there is also a hydro-mechanical hybrid reverse drive type R2 gear output by the rear planetary row. The invention has 2 hydraulic mechanical hybrid reverse gear transmission forms.

Claims (3)

1. The utility model provides a many separation and reunion formula hydraulic machinery buncher of double row planet, its characterized in that: comprises a hydraulic transmission assembly, a mechanical transmission assembly, an input shaft (15) and an output shaft (22) which are arranged in parallel; the hydraulic transmission assembly comprises a variable displacement hydraulic pump (6) and a quantitative hydraulic motor (37) which are arranged in series, a hydraulic motor shaft (19) is arranged at the output end of the quantitative hydraulic motor (37), and the hydraulic motor shaft (19) is arranged in parallel to an input shaft (15) and an output shaft (22); the mechanical transmission assembly comprises a front planet row confluence device, a rear planet row confluence device, a fixed-axis gear pair and a section changing device, wherein the front planet row confluence device comprises a front sun gear (36) fixedly arranged on a hydraulic motor shaft (19), a front gear ring (30) rotatably arranged on the hydraulic motor shaft (19), a plurality of front planet gears (34) arranged between the front sun gear (36) and the front gear ring (30) in a matched mode, and a front planet carrier (35) rotatably arranged on the hydraulic motor shaft (19) and matched with the plurality of front planet gears (34), the rear planet row confluence device comprises a rear sun gear (18) fixedly arranged on the hydraulic motor shaft (19), a rear gear ring (11) rotatably arranged on the hydraulic motor shaft (19), a plurality of rear planet gears (16) arranged between the rear sun gear (18) and the rear gear ring (11) in a matched mode, and a rear planet carrier (16) rotatably arranged on the hydraulic motor shaft (19) and matched with the plurality of rear planet gears (16) 17) The fixed-shaft gear pair comprises a second gear (1) which is rotatably arranged on a hydraulic motor shaft (19) and is fixedly connected with a front planet carrier (35), a first gear (2) and a third gear (33) which are respectively meshed with the second gear (1), a fifth gear (5) which is rotatably arranged on the hydraulic motor shaft (19) and is fixedly connected with a front gear ring (30), a fourth gear (4) and a sixth gear (31) which are respectively meshed with the fifth gear (5), a seventh gear (8) which is fixedly arranged on an input shaft (15), a hydraulic pump gear (7) and an idle gear (9) which are respectively meshed with the seventh gear (8), a tenth gear (20) which is rotatably arranged on the hydraulic motor shaft (19) and is fixedly connected with a rear gear ring (11), and a ninth gear (12) and an eleventh gear (25) which are respectively meshed with the tenth gear (20), A thirteenth gear (21) which is rotationally arranged on a hydraulic motor shaft (19) and is fixedly connected with a rear planet carrier (17), and a twelfth gear (14) and a fourteenth gear (23) which are respectively meshed with the thirteenth gear (21), wherein a first gear (2), a fourth gear (4), a ninth gear (12) and the twelfth gear (14) are respectively rotationally arranged on an input shaft (15), a third gear (33), a sixth gear (31), an eleventh gear (25) and a fourteenth gear (23) are respectively rotationally arranged on an output shaft (22), a hydraulic pump gear (7) is fixedly arranged at the input end of the variable displacement hydraulic pump (6), and a section changing device comprises a first synchronizer (3) for controlling the clutch between the first gear (2) and the fourth gear (4) and the input shaft (15), and a second synchronizer (3) for controlling the clutch between the ninth gear (12) and the twelfth gear (14) and the input shaft (15) 13) A third synchronizer (32) for controlling the clutch between the third gear (33) and the sixth gear (31) and the output shaft (22), a fourth synchronizer (24) for controlling the clutch between the eleventh gear (25) and the fourteenth gear (23) and the output shaft (22) and a clutch assembly, wherein the clutch assembly comprises a shell rotationally arranged on the hydraulic motor shaft (19), a front ring gear clutch (29) for controlling the clutch between the front ring gear (30) and the shell, a front planet carrier clutch (28) for controlling the clutch between the front planet carrier (35) and the shell, a rear planet carrier clutch (27) for controlling the clutch between the rear planet carrier (17) and the shell and a rear ring gear clutch (26) for controlling the clutch between the rear ring gear (11) and the shell, an eighth gear (10) is fixedly arranged on the shell, and the eighth gear (10) is in transmission connection with the idle gear (9).
2. The double-row planetary multi-segment multi-clutch hydromechanical continuously variable transmission of claim 1, wherein: and one end of the input shaft (15) close to the front planet row confluence device is used for being connected with an engine, and one end close to the rear planet row confluence device is used for being connected with a power output device.
3. The double-row planetary multi-segment multi-clutch hydromechanical continuously variable transmission of claim 1, wherein: the hydraulic motor is characterized in that a first hollow shaft and a second hollow shaft are arranged on the hydraulic motor shaft (19) in a rotating mode, a third hollow shaft is arranged on the periphery of the first hollow shaft in a rotating mode, a fourth hollow shaft is arranged on the periphery of the second hollow shaft in a rotating mode, one end of the first hollow shaft is fixedly connected with the second gear (1), the middle of the first hollow shaft is fixedly connected with the front planet carrier (35), the other end of the first hollow shaft is connected with the front planet carrier clutch (28), one end of the second hollow shaft is fixedly connected with the thirteenth gear (21), the middle of the second hollow shaft is fixedly connected with the rear planet carrier (17), the other end of the second hollow shaft is connected with the rear planet carrier clutch (27), one end of the third hollow shaft is fixedly connected with the fifth gear (5), the middle of the third hollow shaft is fixedly connected with the front gear ring (30), and the other end of the third hollow shaft is connected with the front gear clutch (29), one end of the fourth hollow shaft is fixedly connected with the tenth gear (20), the middle part of the fourth hollow shaft is fixedly connected with the rear gear ring (11), and the other end of the fourth hollow shaft is connected with the rear gear ring clutch (26).
CN201810306712.4A 2018-04-08 2018-04-08 Multi-section multi-clutch type hydraulic mechanical continuously variable transmission with double planet rows Expired - Fee Related CN108533701B (en)

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Publication number Priority date Publication date Assignee Title
CN109185417B (en) * 2018-09-27 2021-05-25 江苏大学 Quick reversing power-dividing hydraulic mechanical stepless speed changer
CN109764123B (en) * 2019-01-16 2021-06-22 江苏大学 Multi-mode switching power transmission system with variable characteristic parameters of planetary gear
CN111207198B (en) * 2020-01-20 2021-06-18 江苏大学 Multi-mode mechanical-hydraulic composite transmission device integrating gear, hydraulic pressure and metal belt
CN114087334B (en) * 2021-11-17 2023-11-03 浙江盘毂动力科技有限公司 Hydraulic mechanical combined type comprehensive transmission device and vehicle

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WO2016046730A1 (en) * 2014-09-22 2016-03-31 Rostamlou Alireza Geared continuously variable transmission
CN106369136A (en) * 2016-12-07 2017-02-01 重庆大学 Two-section hydraulic and mechanical compound stepless transmission device
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JP4948288B2 (en) * 2007-06-28 2012-06-06 ヤンマー株式会社 Transmission comprising a hydraulic-mechanical continuously variable transmission
WO2016046730A1 (en) * 2014-09-22 2016-03-31 Rostamlou Alireza Geared continuously variable transmission
CN106369136A (en) * 2016-12-07 2017-02-01 重庆大学 Two-section hydraulic and mechanical compound stepless transmission device
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CN107869563A (en) * 2017-11-21 2018-04-03 河南科技大学 A kind of multistage multi-mode mechanical and hydraulic continuously variable transmission

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