WO2022016607A1 - 一种功率分流和功率汇流相结合的机液复合传动装置 - Google Patents

一种功率分流和功率汇流相结合的机液复合传动装置 Download PDF

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Publication number
WO2022016607A1
WO2022016607A1 PCT/CN2020/106687 CN2020106687W WO2022016607A1 WO 2022016607 A1 WO2022016607 A1 WO 2022016607A1 CN 2020106687 W CN2020106687 W CN 2020106687W WO 2022016607 A1 WO2022016607 A1 WO 2022016607A1
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Prior art keywords
clutch
power
hydraulic
transmission
brake
Prior art date
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Ceased
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PCT/CN2020/106687
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English (en)
French (fr)
Inventor
蔡英凤
朱镇
陈龙
田翔
王骏骋
夏长高
韩江义
王峰
徐兴
施德华
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Jiangsu University
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Jiangsu University
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Publication date
Application filed by Jiangsu University filed Critical Jiangsu University
Priority to US17/623,932 priority Critical patent/US11614151B2/en
Priority to CH70428/21A priority patent/CH717779B1/de
Priority to DE112020001539.4T priority patent/DE112020001539T5/de
Priority to GB2200316.4A priority patent/GB2600578B/en
Publication of WO2022016607A1 publication Critical patent/WO2022016607A1/zh
Anticipated expiration legal-status Critical
Ceased 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
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • 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
    • 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
    • F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
    • 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2053—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with nine engaging means

Definitions

  • the invention relates to the field of gearboxes, in particular to a machine-hydraulic composite transmission device combining power splitting and power confluence.
  • the machine-hydraulic composite transmission device formed by the parallel connection of the hydraulic transmission mechanism and the mechanical transmission mechanism is mainly divided into two types: power split and power confluence.
  • the power splitter-hydraulic compound transmission mechanism adopts a planetary gear mechanism for power splitting at the input end, and has the characteristics of a wide range of speed regulation; Controllability is easier.
  • the multi-mode machine-hydraulic composite transmission device integrating hydraulic transmission, machine-hydraulic transmission and mechanical transmission can only meet the requirements of starting, operating and transitioning of vehicles to a certain extent, but it is still difficult to meet the requirements of fine operation.
  • the present invention provides a machine-hydraulic composite transmission device combining power splitting and power confluence, and provides a hydraulic transmission, a power splitter hydraulic transmission, a power confluence machine hydraulic transmission and a mechanical transmission.
  • the integrated multi-mode machine-hydraulic composite transmission meets the requirements of multi-working conditions and fine work.
  • the present invention achieves the above technical purpose through the following technical means.
  • a mechanical-hydraulic composite transmission device combining power splitting and power convergence comprising an input member, a power splitting mechanism, a mechanical transmission mechanism, a power convergence mechanism, an output member, a hydraulic transmission mechanism, a clutch assembly and a brake assembly; the input member and the The power splitting mechanism is connected, the power converging mechanism is connected with the output member, the clutch assembly connects the output end of the power splitting mechanism to the input end of the mechanical transmission mechanism and the input end of the hydraulic transmission mechanism respectively, and the power confluence
  • the input of the mechanism is connected to the output of the mechanical transmission mechanism and the output of the hydraulic transmission mechanism, respectively; the clutch assembly and the brake assembly provide a continuous transmission ratio between the input member and the output member.
  • the transmission modes provided between the input member and the output member include: hydraulic transmission, power splitter hydraulic transmission, power combiner Hydraulic and mechanical transmissions.
  • the mechanical transmission mechanism includes a mechanical transmission mechanism input shaft, a front planetary gear mechanism and a rear planetary gear mechanism, and the sun gear of the rear planetary gear mechanism and the ring gear of the front planetary gear mechanism are respectively connected with the mechanical transmission mechanism input shaft; the planet carrier of the front planetary gear mechanism is connected with the planet carrier of the rear planetary gear mechanism;
  • the power splitting mechanism includes a power splitting planetary gear mechanism, the ring gear of the power splitting planetary gear mechanism is connected with the input member, and the sun gear of the power splitting planetary gear mechanism is connected with the input end of the hydraulic transmission mechanism, so the The planet carrier of the power distribution planetary gear mechanism is connected with the input shaft of the mechanical transmission mechanism;
  • the power converging mechanism includes a power converging planetary gear mechanism, the ring gear of the rear planetary gear mechanism is connected with the ring gear of the power converging planetary gear mechanism; the planet carrier of the power converging planetary gear mechanism is connected with the output member, The sun gear of the power confluence planetary gear mechanism is connected with the output end of the hydraulic transmission mechanism.
  • the clutch assembly includes a clutch C 2 , a clutch C 4 , a clutch C 5 and a clutch C 6 ; the clutch C 2 selectively divides the power between the ring gear of the planetary gear mechanism and the power splitting planetary gear mechanism frame connected for common rotation; C 4 selectivity of the clutch of the power bus and the planetary gear mechanism of the planetary carrier power bus means connected for common rotation; the selective clutch C 5 fraction of the power the sun gear and the input hydraulic actuators pop star-wheel mechanism is connected for common rotation; the output of the clutch C 6 selective hydraulic actuator power bus with the sun gear of the planetary gear mechanism connected for common rotation; the The brake assembly includes a brake B 1 , a brake B 2 and a brake B 3 , the brake B 1 is used to selectively connect the planet carrier of the front planetary gear mechanism to the fixed part; the brake B 2 is used to selectively connect the the front sun gear of the planetary gear mechanism connected to a fixed member; said brake B 3 for the ring gear selectively power bus planetary gear mechanism connected to a fixed member
  • the clutch assembly further includes a clutch C 3 , the clutch C 3 selectively connects the ring gear of the front planetary gear mechanism with the sun gear of the front planetary gear mechanism for common rotation;
  • Engaging said clutch C 4 , clutch C 5 , clutch C 6 and brake B 1 provides power splitter hydraulic transmission between the input member and the output member in the reverse direction;
  • engaging the clutch C 2 , the clutch C 5 , the clutch C 6 and the brake B 1 provides hydraulic transmission of power in the reverse direction between the input member and the output member;
  • Engaging the clutch C 2 , clutch C 4 and brake B 2 , and engaging the clutch C 2 , clutch C 3 and clutch C 4 respectively provide mechanical transmissions between the input member and the output member in different forward directions.
  • the machine-hydraulic composite transmission device combining power splitting and power confluence according to the present invention is a machine-hydraulic composite transmission device integrating hydraulic transmission, machine-hydraulic transmission and mechanical transmission.
  • the machine-hydraulic composite transmission device of the present invention that combines power splitting and power confluence, the power splitting machine-hydraulic transmission and the power converging machine-hydraulic transmission in the machine-hydraulic transmission meet the requirements of fine work.
  • the machine-hydraulic composite transmission device of the present invention which combines power splitting and power confluence, adopts a one-way variable pump to control the quantitative motor mechanism and the transmission device structure to realize the positive and negative transmission of the mechanism.
  • the mechanical-hydraulic composite transmission device of the present invention which combines power splitting and power confluence, adopts less clutch components and brake components to meet the switching from hydraulic transmission to mechanical-hydraulic transmission.
  • FIG. 1 is a schematic diagram of the mechanical-hydraulic composite transmission device combining power splitting and power confluence according to the present invention.
  • FIG. 2 is a schematic diagram of the power flow of the R(H) gear according to the present invention.
  • Fig. 3 is the schematic diagram of F 1 (H) gear power flow of the present invention.
  • FIG. 6 is a schematic diagram of the power flow of the F 1 (HMs) gear of the present invention.
  • FIG. 10 is a schematic diagram of the power flow of the F 2 (HMv) gear of the present invention.
  • FIG. 11 is a schematic diagram of the power flow of the R(M) gear of the present invention.
  • FIG. 12 is a schematic diagram of the power flow of the F 1 (M) gear of the present invention.
  • FIG. 13 is a schematic diagram of the power flow of the F 2 (M) gear of the present invention.
  • Figure 14 is a graph of the speed regulation characteristic of the present invention.
  • the mechanical-hydraulic composite transmission device combining power splitting and power confluence includes a main clutch C 1 2 , an input shaft 1 , a power splitting mechanism 3 , a mechanical transmission mechanism 4 , and a power converging mechanism 5 . , the output shaft 6 and the hydraulic transmission mechanism 7 .
  • Power split mechanism 3 includes a power split mechanism input shaft 31, the clutch C 2 32, ring gear 33 of power split mechanism, a planetary carrier 34 of the power split mechanism and a power split mechanism the sun gear 35, the ring gear 33 of power split mechanism and a power split mechanism
  • the input shaft 31 is fixedly connected, and is connected with the input shaft 1 through the main clutch C 1 2;
  • the clutch C 2 32 is used to connect the power split mechanism ring gear 33 and the power split mechanism planet carrier 34 together;
  • the power split mechanism sun gear 35 and The input end of the hydraulic transmission mechanism 7 is connected;
  • the power splitting mechanism planet carrier 34 is connected with the mechanical transmission mechanism 4;
  • the mechanical transmission mechanism 4 includes a mechanical transmission mechanism input shaft 41 , a clutch C 3 42 , a brake B 2 43 , a front planetary gear mechanism sun gear 44 , a front planetary gear mechanism planet carrier 45 , a brake B 1 46 , and a rear planetary gear mechanism planet carrier 47 ,
  • the sun gear 410 of the rear planetary gear mechanism, the ring gear 48 of the front planetary gear mechanism and the planet carrier 34 of the power split mechanism are respectively fixedly connected with the input shaft 41 of the mechanical transmission mechanism;
  • the clutch C 3 42 is used to connect the sun gear of the front planetary gear mechanism 44 and the front planetary gear mechanism ring gear 48,
  • the brake B 2 43 is used to fix the front planetary gear mechanism sun gear 44;
  • the front planetary gear mechanism planet carrier 45 and the rear planetary gear mechanism planet carrier 47 are fixed, and can be fixed by the brake B 1 46 is fixed;
  • the rear planetary gear ring gear 49 is fixedly connected with the output shaft 411 of the mechanical transmission mechanism, and is connected with the power confluence mechanism 5;
  • the power transfer mechanism 5 includes a brake B 3 51 , a power transfer mechanism ring gear 52 , a power transfer mechanism planet carrier 53 , a power transfer mechanism sun gear 54 and a clutch C 4 55 .
  • the power confluence mechanism ring gear 52 is fixedly connected with the output shaft 411 of the mechanical transmission mechanism, and can be fixed by the brake B 3 51 ;
  • the power confluence mechanism planet carrier 53 is fixedly connected with the output shaft 6 , and is connected to the power confluence through the clutch C 4 55
  • the mechanism ring gear 52 is connected;
  • the power confluence mechanism sun gear 54 is connected with the output end of the hydraulic transmission mechanism 7 .
  • the hydraulic transmission mechanism 7 includes a clutch C 5 71 , a hydraulic transmission input gear pair 72 , a variable pump 73 , a hydraulic pipeline 74 , a constant displacement motor 75 , a hydraulic transmission output gear pair 76 and a clutch C 6 77 .
  • the power transmitted by the power splitting mechanism 3 is transmitted to the variable pump 73 through the hydraulic transmission input gear pair 72 and the clutch C 5 71.
  • the variable pump 73 outputs oil to the quantitative motor 75 through the hydraulic pipeline 74, and drives the quantitative motor 75 to rotate.
  • the quantitative motor 75 The power is transmitted to the output shaft 6 through the clutch C 6 77 , the hydraulic transmission output gear pair 76 and the power combining mechanism 5 .
  • the transmission modes provided between the engine and the output member include: hydraulic transmission and power splitter hydraulic transmission , Power consolidator hydraulic transmission and mechanical transmission.
  • Hydraulic transmission includes R(H), F 1 (H) and F 2 (H) gears as follows:
  • the power flow of R(H) gear is shown in Figure 2.
  • the clutch C 5 71, the clutch C 6 77, the brake B 1 46 and the brake B 2 43 are engaged, the engine power transmitted after the main clutch C 12 is engaged, passes through the power split mechanism input shaft 31, the power split mechanism ring gear 33, The power split mechanism sun gear 35 , the hydraulic transmission mechanism 7 , the power merge mechanism sun gear 54 and the power merge mechanism planet carrier 53 are output from the output shaft 6 .
  • the relationship between the output speed and the input speed is:
  • n I is the input speed
  • n o is the output speed
  • e is the displacement ratio of the hydraulic transmission mechanism.
  • the power flow of the F 2 (H) gear is shown in Figure 4.
  • the clutch C 2 32, the clutch C 4 55, the clutch C 5 71 and the clutch C 6 77 are engaged, the power splitting mechanism 3 and the power converging mechanism 5 are respectively fixed as a whole, and the engine power transmitted after the main clutch C 1 2 is engaged, passes through The power split mechanism 3 , the hydraulic transmission mechanism 7 and the power merge mechanism 5 are output from the output shaft 6 .
  • the relationship between the output speed and the input speed is:
  • the power splitter hydraulic transmission includes R (HMs), F 1 (HMs) and F 2 (HMs) as follows:
  • the power flow of the R(HMs) gear is shown in Figure 5.
  • the clutch C 4 55, the clutch C 5 71, the clutch C 6 77 and the brake B 1 46 are engaged, the engine power transmitted after the main clutch C 12 is engaged, passes through the input shaft 31 of the power split mechanism and the ring gear 33 of the power split mechanism.
  • Divided into two paths one is transmitted to the sun gear 54 of the power confluence mechanism through the power splitting mechanism sun gear 35 and the hydraulic transmission mechanism 7, and the other is passed through the power splitting mechanism planet carrier 34, the mechanical transmission mechanism input shaft 41, and the mechanical transmission mechanism rear sun gear 410 ,
  • the rear gear 49 of the mechanical transmission mechanism and the output shaft 411 of the mechanical transmission mechanism are transmitted to the ring gear 52 of the power confluence mechanism.
  • the hydraulic power transmitted to the sun gear 54 of the power confluence mechanism is transmitted to the power confluence mechanism.
  • the mechanical power of the power transfer mechanism ring gear 52 is output from the output shaft 6 via the power transfer mechanism 5 .
  • the relationship between the output speed and the input speed is:
  • the F 1 (HMs) gear power flow is shown in Figure 6.
  • the clutch C 4 55, the clutch C 5 71, the clutch C 6 77 and the brake B 2 43 are engaged, the engine power transmitted after the main clutch C 1 2 is engaged, passes through the input shaft 31 of the power split mechanism and the ring gear 33 of the power split mechanism. Divided into two paths, one is transmitted to the sun gear 54 of the power confluence mechanism through the sun gear 35 of the power split mechanism and the hydraulic transmission mechanism 7, and the other is transmitted to the input shaft 41 of the mechanical transmission mechanism through the planet carrier 34 of the power split mechanism.
  • the mechanical power flow is again Diverted, all the way through the front ring gear 48 of the mechanical transmission mechanism and the front planetary carrier 45 of the mechanical transmission mechanism, transmitted to the rear planetary carrier 47 of the mechanical transmission mechanism, and directly transmitted to the rear sun gear 410 of the mechanical transmission mechanism, two mechanical power flows in the mechanical transmission mechanism.
  • the rear gear ring 49 converges, and is transmitted to the power confluence mechanism ring gear 52 through the mechanical transmission mechanism output shaft 411. Since the power confluence mechanism 5 is firmly connected as a whole, the hydraulic power transmitted to the power confluence mechanism sun gear 54 is transmitted to the power confluence mechanism.
  • the mechanical power of the power combining mechanism ring gear 52 is output from the output shaft 6 via the power combining mechanism 5 . At this time, the relationship between the output speed and the input speed is:
  • the power flow of the F 2 (HMs) gear is shown in Figure 7.
  • the clutch C 3 42 , the clutch C 4 55 , the clutch C 5 71 and the clutch C 6 77 are engaged, the engine power transmitted after the main clutch C 1 2 is engaged, passes through the input shaft 31 of the power split mechanism and the ring gear 33 of the power split mechanism. Divided into two paths, one is transmitted to the sun gear 54 of the power confluence mechanism through the power shunt mechanism sun gear 35 and the hydraulic transmission mechanism 7, and the other is transmitted to the power confluence mechanism ring gear 52 through the fixed mechanical transmission mechanism 4.
  • the mechanism 5 is firmly connected as a whole, so the hydraulic power transmitted to the sun gear 54 of the power merge mechanism and the mechanical power transmitted to the ring gear 52 of the power merge mechanism are output from the output shaft 6 through the power merge mechanism 5 .
  • the relationship between the output speed and the input speed is:
  • the hydraulic transmission of the power consolidator includes the R (HMv) gear, the F 1 (HMv) gear and the F 2 (HMv) gear, as follows:
  • the power flow of the R(HMv) gear is shown in Figure 8.
  • the clutch C 2 32 , the clutch C 5 71 , the clutch C 6 77 and the brake B 1 46 are engaged, the engine power transmitted after the main clutch C 1 2 is engaged is divided into two paths through the fixed power splitting mechanism 3 . , all the way through the hydraulic transmission mechanism 7 to the sun gear 54 of the power confluence mechanism, all the way through the mechanical transmission mechanism input shaft 41, the mechanical transmission mechanism rear sun gear 410, the mechanical transmission mechanism rear gear 49 and the mechanical transmission mechanism output shaft 411, transmitted to the The power transfer mechanism ring gear 52, the hydraulic power transmitted to the power transfer mechanism sun gear 54 and the mechanical power transferred to the power transfer mechanism ring gear 52 are output from the output shaft 6 through the power transfer mechanism planet carrier 53.
  • the relationship between the output speed and the input speed is:
  • the F 1 (HMv) gear power flow is shown in Figure 9.
  • the clutch C 2 32, the clutch C 5 71, the clutch C 6 77 and the brake B 2 43 are engaged, the engine power transmitted after the main clutch C 1 2 is engaged is divided into two paths after the power splitting mechanism 3 which is fixedly connected as a whole , all the way through the hydraulic transmission mechanism 7 to the sun gear 54 of the power confluence mechanism, and all the way to the input shaft 41 of the mechanical transmission mechanism.
  • the mechanical power flow is divided again, and all the way through the front gear ring 48 of the mechanical transmission mechanism and the front planetary carrier of the mechanical transmission mechanism 45.
  • the F 2 (HMv) gear power flow is shown in Figure 10.
  • the clutch C 2 32 , the clutch C 3 42 , the clutch C 5 71 and the clutch C 6 77 are engaged, the engine power transmitted after the main clutch C 1 2 is engaged is divided into two paths after the power splitting mechanism 3 that is firmly connected as a whole , all the way through the hydraulic transmission mechanism 7 is transmitted to the sun gear 54 of the power confluence mechanism, and all the way through the mechanical transmission mechanism 4 that is fixed as a whole to the power confluence mechanism ring gear 52, and is transmitted to the hydraulic power flow and transmission of the sun gear 54 of the power confluence mechanism.
  • the mechanical power to the power combiner ring gear 52 is combined to the power combiner carrier 53 and output from the output shaft 6 .
  • the relationship between the output speed and the input speed is:
  • Mechanical transmission comprises a R (M) speed, F 1 (M) gear and F 2 (M) file, as follows:
  • the power flow of the R(M) gear is shown in Figure 11.
  • the input shaft 41 of the mechanical transmission mechanism, the rear sun gear 410 of the mechanical transmission mechanism, the rear gear ring 49 of the mechanical transmission mechanism, the output shaft 411 of the mechanical transmission mechanism and the power confluence mechanism 5 are output from the output shaft 6 .
  • the relationship between the output speed and the input speed is:
  • n o -0.4n I .
  • the power flow of the F 1 (M) gear is shown in Figure 12.
  • the master clutch C is transmitted after 12 engaging a power bus means 5, via the power split mechanism 3 It is split with the input shaft 41 of the mechanical transmission mechanism, and all the way is directly transmitted to the rear sun gear 410 of the mechanical transmission mechanism.
  • the mechanical power flows through the mechanical transmission mechanism, after the ring gear 49 converges, it is output from the output shaft 6 through the output shaft 411 of the mechanical transmission mechanism and the power confluence mechanism 5 .
  • the relationship between the output speed and the input speed is:
  • n o 0.5n I .
  • the power flow of the F 2 (M) gear is shown in Figure 13.
  • the clutch C 2 32, the clutch C 3 42 and the clutch C 4 55 are engaged, the power split mechanism 3, the mechanical transmission mechanism 4 and the power merge mechanism 5 are each firmly connected as a whole, and the engine power transmitted after the main clutch C 1 2 is engaged, It is output from the output shaft 6 through the power split mechanism 3 , the mechanical transmission mechanism 4 and the power confluence mechanism 5 .
  • the relationship between the output speed and the input speed is:
  • n o n I .
  • n o is the output shaft speed
  • n e is the engine speed
  • e is the displacement ratio of the hydraulic transmission mechanism
  • i is the relevant gear ratio
  • k s is the characteristic parameter of the power split planetary gear
  • k v is the power confluence flow Star gear characteristic parameters
  • k f is the characteristic parameter of the front planetary gear mechanism
  • k r is the characteristic parameter of the rear planetary gear mechanism
  • the speed regulation characteristic curve of the present invention is shown in FIG. 14 .
  • the speed regulation range of R(H) gear is n o ⁇ (-0.78, 0)n I
  • the speed regulation range of F 1 (H) gear is n o ⁇ ( 0, 0.22)n I
  • F 2 (H) gear speed range is no o ⁇ (0, 1.00)n I
  • the R(HMs) gear speed range is is no o ⁇ (-0.29, 0)n I
  • the F 1 (HMs) gear speed regulation range is no o ⁇ (0.44, 0.70)n I
  • F 2 (HMs ) gear speed regulation range is n o ⁇ (1.00, 7.00)n I
  • the R(HMs) gear speed regulation range is n o ⁇ (-0.31, -0.09)n I
  • F 1 (HMs) gear speed regulation range is n o ⁇ (-0.31, -0.09)n I
  • F 1 (HMs) gear speed regulation range is n
  • the F 1 (H) gear mainly adopts low speed and high torque to meet the working conditions with high power requirements.
  • the F 2 (H) gear can be used for both It can be used to connect the F 1 (HMs) gear and F 2 (HMs) gear of the hydraulic transmission of the power splitter, and can also be used to connect the F 1 (HMv) gear and F 2 (HMv) gear of the hydraulic transmission of the power combiner to achieve Stepless speed regulation.
  • the hydraulic transmission mechanism can be adjusted 7 gear ratio and selective control of the clutch C 1 (2), clutch C 2 32, clutch C 3 42, clutch C 4 55, clutch C 5 71, clutch C 6 77, brake B 1 46 and brake B 2
  • the engagement of 43 realizes stepless speed regulation.
  • the hydraulic transmission adopts the R(H) gear to connect the R(HMs) gear of the hydraulic transmission of the power splitter and the R(HMv) gear of the hydraulic transmission of the power concentrator to realize stepless speed regulation.
  • the clutch C 1 2 and the clutch C 2 32 can be selectively controlled by adjusting the transmission ratio of the hydraulic transmission mechanism 7 , clutch C 3 42, clutch C 4 55, clutch C 5 71, clutch C 6 77, brake B 1 46 and brake B 2 43 are engaged to realize stepless speed regulation.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

本发明提供了一种功率分流和功率汇流相结合的机液复合传动装置，包括输入构件、功率分流机构、机械传动机构、功率汇流机构、输出构件、液压传动机构、离合器组件和制动器组件；所述输入构件与功率分流机构连接，所述功率汇流机构与输出构件连接，所述离合器组件将所述功率分流机构的输出端分别连接到机械传动机构的输入端和液压传动机构的输入端，将所述功率汇流机构的输入端分别连接到机械传动机构的输出端和液压传动机构的输出端；所述离合器组件和制动器组件提供输入构件与输出构件之间连续的传动比。本发明提供一种集液压传动、功率分流机液传动、功率汇流机液传动和机械传动为一体的多模式机液复合传动装置，满足多工况精细作业的要求。

Description

一种功率分流和功率汇流相结合的机液复合传动装置 技术领域
本发明涉及变速箱领域，特别涉及一种功率分流和功率汇流相结合的机液复合传动装置。
背景技术
由液压传动机构和机械传动机构并联形成的机液复合传动装置主要分为功率分流和功率汇流两种类型。一般而言，功率分流机液复合传动机构采用行星齿轮机构在输入端进行功率分流，具有调速范围较宽的特点；功率汇流机液复合传动机构采用行星齿轮机构在输出端进行功率汇流，具有可控性较容易的特点。集液压传动、机液传动和机械传动为一体的多模式机液复合传动装置在某种程度上只能适合车辆的起步、作业和转场要求，对于精细化作业要求则尚难满足。
发明内容
针对现有技术中存在的不足，本发明提供了一种功率分流和功率汇流相结合的机液复合传动装置，提供一种集液压传动、功率分流机液传动、功率汇流机液传动和机械传动为一体的多模式机液复合传动装置，满足多工况精细作业的要求。
本发明是通过以下技术手段实现上述技术目的的。
一种功率分流和功率汇流相结合的机液复合传动装置，包括输入构件、功率分流机构、机械传动机构、功率汇流机构、输出构件、液压传动机构、离合器组件和制动器组件；所述输入构件与功率分流机构连接，所述功率汇流机构与输出构件连接，所述离合器组件将所述功率分流机构的输出端分别连接到机械传动机构的输入端和液压传动机构的输入端，将所述功率汇流机构的输入端分别连接到机械传动机构的输出端和液压传动机构的输出端；所述离合器组件和制动器组件提供输入构件与输出构件之间连续的传动比。
进一步，通过调节液压传动机构的排量比和选择性控制所述离合器组件和制动器组件的接合，提供输入构件与输出构件之间的传动方式包括：液压传动、功率分流机液传动、功率汇流机液传动和机械传动。
进一步，所述机械传动机构包括机械传动机构输入轴、前行星齿轮机构和后行星齿轮机构，所述后行星齿轮机构的太阳轮和前行星齿轮机构的齿圈分别与机械传动机构输入轴连接；所述前行星齿轮机构的行星架和后行星齿轮机构的行星架连接；
所述功率分流机构包括功率分流行星轮机构，所述功率分流行星轮机构的齿圈与输入构件连接，所述功率分流行星轮机构的太阳轮与液压传动机构的输入端连接，所述功率分流行 星轮机构的行星架与机械传动机构输入轴连接；
所述功率汇流机构包括功率汇流行星轮机构，所述后行星齿轮机构的齿圈与功率汇流行星轮机构的齿圈连接；所述功率汇流行星轮机构的行星架与输出构件连接，所述功率汇流行星轮机构的太阳轮与液压传动机构的输出端连接。
进一步，所述离合器组件包括离合器C 2、离合器C 4、离合器C 5和离合器C 6；所述离合器C 2选择性的将功率分流行星轮机构的齿圈与功率分流行星轮机构的行星架连接以共同旋转；所述离合器C 4选择性的将功率汇流行星轮机构的齿圈与功率汇流行星轮机构的行星架连接以共同旋转；所述离合器C 5选择性的将功率分流行星轮机构的太阳轮与液压传动机构的输入端连接以共同旋转；所述离合器C 6选择性的将液压传动机构的输出端与功率汇流行星轮机构的太阳轮连接以共同旋转；所述制动器组件包括制动器B 1、制动器B 2和制动器B 3，所述制动器B 1用于选择性的将前行星齿轮机构的行星架连接到固定件；所述制动器B 2用于选择性的将前行星齿轮机构的太阳轮连接到固定件；所述制动器B 3用于选择性的将功率汇流行星轮机构的齿圈连接到固定件；通过调节液压传动机构的排量比和选择性控制所述离合器C 2、离合器C 4、离合器C 5、离合器C 6、制动器B 1、制动器B 2和制动器B 3的接合，提供输入构件与输出构件之间的连续前进或后退的液压传动。
进一步，接合所述离合器C 5、离合器C 6、制动器B 1和制动器B 2，提供输入构件与输出构件之间后退方向的液压传动；
接合所述离合器C 5、离合器C 6、离合器C 2和制动器B 3，接合所述离合器C 5、离合器C 6、离合器C 2和离合器C 4，分别提供输入构件与输出构件之间前进方向各自相异的液压传动。
进一步，所述离合器组件还包括离合器C 3，所述离合器C 3选择性的将前行星齿轮机构的齿圈与前行星齿轮机构的太阳轮连接以共同旋转；
接合所述离合器C 4、离合器C 5、离合器C 6和制动器B 1提供输入构件与输出构件之间后退方向的功率分流机液传动；
接合所述离合器C 4、离合器C 5、离合器C 6和制动器B 2，接合所述离合器C 3、离合器C 4、离合器C 5和离合器C 6，分别提供输入构件与输出构件之间前进方向各自相异的功率分流机液传动。
进一步，接合所述离合器C 2、离合器C 5、离合器C 6和制动器B 1提供输入构件与输出构件之间后退方向的功率汇流机液传动；
接合所述离合器C 2、离合器C 5、离合器C 6和制动器B 2，接合所述离合器C 2、离合器C 3、离合器C 5和离合器C 6，分别提供输入构件与输出构件之间前进方向各自相异的功率汇 流机液传动。
进一步，接合所述离合器C 2、离合器C 4和制动器B 1提供输入构件与输出构件之间后退方向的机械传动；
接合所述离合器C 2、离合器C 4和制动器B 2，接合所述离合器C 2、离合器C 3和离合器C 4，分别提供输入构件与输出构件之间前进方向各自相异的机械传动。
进一步，通过调节液压传动机构7的排量比和选择性控制所述离合器C 1、离合器C 2、离合器C 3、离合器C 4、离合器C 5、离合器C 6、制动器B 1和制动器B 2的接合，提供前进方向的液压传动分别与前进方向的功率分流机液传动和前进方向的功率汇流机液传动之间的无级调速。
进一步，通过调节液压传动机构7的排量比和选择性控制所述离合器C 1、离合器C 2、离合器C 3、离合器C 4、离合器C 5、离合器C 6、制动器B 1和制动器B 2的接合，提供后退方向的液压传动分别与后退方向的功率分流机液传动和后退方向的功率汇流机液传动之间的无级调速。
本发明的有益效果在于：
1.本发明所述的功率分流和功率汇流相结合的机液复合传动装置，为一款集液压传动、机液传动和机械传动为一体的机液复合传动装置。
2.本发明所述的功率分流和功率汇流相结合的机液复合传动装置，机液传动中的功率分流机液传动和功率汇流机液传动满足精细化作业要求。
3.本发明所述的功率分流和功率汇流相结合的机液复合传动装置，采用单向变量泵控定量马达机构与传动装置结构相结合，实现机构的正、负向传动。
4.本发明所述的功率分流和功率汇流相结合的机液复合传动装置，采用较少的离合器组件和制动器组件满足液压传动切换到机液传动。
附图说明
图1为本发明所述的功率分流和功率汇流相结合的机液复合传动装置的原理图。
图2为本发明的R(H)档位功率流向示意图。
图3为本发明的F 1(H)档位功率流向示意图；
图4为本发明的F 2(H)档位功率流向示意图；
图5为本发明的R(HMs)档位功率流向示意图；
图6为本发明的F 1(HMs)档位功率流向示意图；
图7为本发明的F 2(HMs)档位功率流向示意图；
图8为本发明的R(HMv)档位功率流向示意图；
图9为本发明的F 1(HMv)档位功率流向示意图；
图10为本发明的F 2(HMv)档位功率流向示意图；
图11为本发明的R(M)档位功率流向示意图；
图12为本发明的F 1(M)档位功率流向示意图；
图13为本发明的F 2(M)档位功率流向示意图；
图14为本发明的调速特性曲线图。
图中：
1-输入轴；2-主离合器C 1；3-功率分流机构；31-功率分流机构输入轴；32-离合器C 2；33-功率分流机构齿圈；34-功率分流机构行星架；35-功率分流机构太阳轮；4-机械传动机构；41-机械传动机构输入轴；42-离合器C 3；43-制动器B 2；44-前行星齿轮机构太阳轮；45-前行星齿轮机构行星架；46-制动器B 1；47-后行星齿轮机构行星架；48-前行星齿轮机构齿圈；49-后行星齿轮机构齿圈；410-后行星齿轮机构太阳轮；411-机械传动机构输出轴；5-功率汇流机构；51-制动器B 3；52-功率汇流机构齿圈；53-功率汇流机构行星架；54-功率汇流机构太阳轮；55-离合器C 4；6-输出轴；7-液压传动机构；71-离合器C 5；72-液压传动输入齿轮副；73-变量泵；74-液压管道；75-定量马达；76-液压传动输出齿轮副；77-离合器C 6。
具体实施方式
下面结合附图以及具体实施例对本发明作进一步的说明，但本发明的保护范围并不限于此。
如图1所示，本发明所述的功率分流和功率汇流相结合的机液复合传动装置，包括主离合器C 1 2、输入轴1、功率分流机构3、机械传动机构4、功率汇流机构5、输出轴6和液压传动机构7。
功率分流机构3包括功率分流机构输入轴31、离合器C 2 32、功率分流机构齿圈33、功率分流机构行星架34和功率分流机构太阳轮35，所述功率分流机构齿圈33与功率分流机构输入轴31固连，并通过主离合器C 1 2与输入轴1连接；离合器C 2 32用于将功率分流机构齿圈33和功率分流机构行星架34连接在一起；功率分流机构太阳轮35与液压传动机构7的输入端连接；功率分流机构行星架34与机械传动机构4连接；
机械传动机构4包括机械传动机构输入轴41、离合器C 3 42、制动器B 2 43、前行星齿轮机构太阳轮44、前行星齿轮机构行星架45、制动器B 1 46、后行星齿轮机构行星架47、前行星齿轮机构齿圈48、后行星齿轮机构齿圈49、后行星齿轮机构太阳轮410和机械传动机构输出轴411。所述后行星齿轮机构太阳轮410、前行星齿轮机构齿圈48和功率分流机构行星架34分别与机械传动机构输入轴41固连；所述离合器C 3 42用于连接前行星齿轮机构太阳轮 44和前行星齿轮机构齿圈48，所述制动器B 2 43用于固定前行星齿轮机构太阳轮44；所述前行星齿轮机构行星架45和后行星齿轮机构行星架47固连，并可由制动器B 146固定；后行星齿轮机构齿圈49与机械传动机构输出轴411固连，并与功率汇流机构5连接；
功率汇流机构5包括制动器B 3 51、功率汇流机构齿圈52、功率汇流机构行星架53、功率汇流机构太阳轮54和离合器C 4 55。所述功率汇流机构齿圈52与机械传动机构输出轴411固连，并可由制动器B 3 51固定；所述功率汇流机构行星架53与输出轴6固连，并通过离合器C 4 55与功率汇流机构齿圈52连接；所述功率汇流机构太阳轮54与液压传动机构7的输出端连接。
液压传动机构7包括离合器C 5 71、液压传动输入齿轮副72、变量泵73、液压管道74、定量马达75、液压传动输出齿轮副76和离合器C 6 77。功率分流机构3传递的动力，经液压传动输入齿轮副72和离合器C 5 71传递给变量泵73，变量泵73通过液压管道74向定量马达75输出油液，带动定量马达75转动，定量马达75的动力经离合器C 6 77、液压传动输出齿轮副76和功率汇流机构5，传递给输出轴6。
如表1所示，通过调节液压传动机构7的排量比和选择性控制所述离合器组件和制动器组件的接合，提供发动机与输出构件之间的传动方式包括：液压传动和功率分流机液传动、功率汇流机液传动和机械传动。
液压传动包括R(H)档、F 1(H)档和F 2(H)档，具体如下：
R(H)档位功率流向如图2所示。当接合离合器C 5 71、离合器C 6 77、制动器B 1 46和制动器B 2 43时，主离合器C 1 2接合后传递的发动机动力，经功率分流机构输入轴31、功率分流机构齿圈33、功率分流机构太阳轮35、液压传动机构7、功率汇流机构太阳轮54和功率汇流机构行星架53，从输出轴6输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106687-appb-000001
式中，n I为输入转速，n o为输出转速，e为液压传动机构的排量比。
F 1(H)档位功率流向如图3所示。当接合离合器C 2 32、离合器C 5 71、离合器C 6 77和制动器B 3 51时，功率分流机构3固连为一体，主离合器C 1 2接合后传递的发动机动力，经功率分流机构3、液压传动机构7、功率汇流机构太阳轮54和功率汇流机构行星架53，从输出轴6输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106687-appb-000002
F 2(H)档位功率流向如图4所示。当接合离合器C 2 32、离合器C 4 55离合器C 5 71和离合器C 6 77时，功率分流机构3和功率汇流机构5分别固连为一体，主离合器C 1 2接合后传 递的发动机动力，经功率分流机构3、液压传动机构7和功率汇流机构5，从输出轴6输出。此时，输出转速与输入转速关系为：
n o＝en I。
功率分流机液传动包括R(HMs)档、F 1(HMs)档和F 2(HMs)档，具体如下：
R(HMs)档位功率流向如图5所示。当接合离合器C 4 55、离合器C 5 71、离合器C 6 77和制动器B 1 46时，主离合器C 1 2接合后传递的发动机动力，经功率分流机构输入轴31和功率分流机构齿圈33后分为两路，一路经功率分流机构太阳轮35和液压传动机构7传递到功率汇流机构太阳轮54，一路经功率分流机构行星架34、机械传动机构输入轴41、机械传动机构后太阳轮410、机械传动机构后齿圈49和机械传动机构输出轴411，传递到功率汇流机构齿圈52，由于功率汇流机构5固连为一体，故传递到功率汇流机构太阳轮54的液压动力与传递到功率汇流机构齿圈52的机械动力，经功率汇流机构5，从输出轴6输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106687-appb-000003
F 1(HMs)档位功率流向如图6所示。当接合离合器C 4 55、离合器C 5 71、离合器C 6 77和制动器B 2 43时，主离合器C 1 2接合后传递的发动机动力，经功率分流机构输入轴31和功率分流机构齿圈33后分为两路，一路经功率分流机构太阳轮35和液压传动机构7传递到功率汇流机构太阳轮54，一路经功率分流机构行星架34传递到机械传动机构输入轴41，此时机械功率流再次分流，一路经机械传动机构前齿圈48和机械传动机构前行星架45，传递到机械传动机构后行星架47，一路直接传递到机械传动机构后太阳轮410，两路机械功率流在机械传动机构后齿圈49处汇流，并经机械传动机构输出轴411传递到功率汇流机构齿圈52，由于功率汇流机构5固连为一体，故传递到功率汇流机构太阳轮54的液压动力与传递到功率汇流机构齿圈52的机械动力，经功率汇流机构5，从输出轴6输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106687-appb-000004
F 2(HMs)档位功率流向如图7所示。当接合离合器C 3 42、离合器C 4 55、离合器C 5 71和离合器C 6 77时，主离合器C 1 2接合后传递的发动机动力，经功率分流机构输入轴31和功率分流机构齿圈33后分为两路，一路经功率分流机构太阳轮35和液压传动机构7传递到功率汇流机构太阳轮54，一路经固连为一体的机械传动机构4传递到功率汇流机构齿圈52，由于功率汇流机构5固连为一体，故传递到功率汇流机构太阳轮54的液压动力与传递到功率汇 流机构齿圈52的机械动力，经功率汇流机构5，从输出轴6输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106687-appb-000005
功率汇流机液传动包括R(HMv)档、F 1(HMv)档和F 2(HMv)档，具体如下：
R(HMv)档位功率流向如图8所示。当接合离合器C 2 32、离合器C 5 71、离合器C 6 77和制动器B 1 46时，主离合器C 1 2接合后传递的发动机动力，经固连为一体的功率分流机构3后分为两路，一路经液压传动机构7传递到功率汇流机构太阳轮54，一路经机械传动机构输入轴41、机械传动机构后太阳轮410、机械传动机构后齿圈49和机械传动机构输出轴411，传递到功率汇流机构齿圈52，传递到功率汇流机构太阳轮54的液压动力与传递到功率汇流机构齿圈52的机械动力，经功率汇流机构行星架53，从输出轴6输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106687-appb-000006
F 1(HMv)档位功率流向如图9所示。当接合离合器C 2 32、离合器C 5 71、离合器C 6 77和制动器B 2 43时，主离合器C 1 2接合后传递的发动机动力，经固连为一体的功率分流机构3后分为两路，一路经液压传动机构7传递到功率汇流机构太阳轮54，一路传递到机械传动机构输入轴41，此时机械功率流再次分流，一路经机械传动机构前齿圈48和机械传动机构前行星架45，传递到机械传动机构后行星架47，一路直接传递到机械传动机构后太阳轮410，两路机械功率流在机械传动机构后齿圈49处汇流，并经机械传动机构输出轴411传递到功率汇流机构齿圈52，传递到功率汇流机构太阳轮54的液压功率流和传递到功率汇流机构齿圈52的机械功率汇流到功率汇流机构行星架53，从输出轴6输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106687-appb-000007
F 2(HMv)档位功率流向如图10所示。当接合离合器C 2 32、离合器C 3 42、离合器C 5 71和离合器C 6 77时，主离合器C 1 2接合后传递的发动机动力，经固连为一体的功率分流机构3后分为两路，一路经液压传动机构7传递到功率汇流机构太阳轮54，一路经固连为一体的机械传动机构4传递到功率汇流机构齿圈52，传递到功率汇流机构太阳轮54的液压功率流和传递到功率汇流机构齿圈52的机械功率汇流到功率汇流机构行星架53，从输出轴6输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106687-appb-000008
机械传动包括R(M)档、F 1(M)档和F 2(M)档，具体如下：
R(M)档位功率流向如图11所示。当接合离合器C 2 32、离合器C 4 55和制动器B 1 46时，功率分流机构3和功率汇流机构5各自固连为一体，主离合器C 1 2接合后传递的发动机动力，经功率分流机构3、机械传动机构输入轴41、机械传动机构后太阳轮410、机械传动机构后齿圈49、机械传动机构输出轴411和功率汇流机构5，从输出轴6输出。此时，输出转速与输入转速关系为：
n o＝-0.4n I。
F 1(M)档位功率流向如图12所示。当接合离合器C 2 32、离合器C 4 55和制动器B 2 43时，功率分流机构3和功率汇流机构5各自固连为一体，主离合器C 1 2接合后传递的发动机动力，经功率分流机构3和机械传动机构输入轴41后分流，一路直接传递到机械传动机构后太阳轮410，一路经机械传动机构前齿圈48、机械传动机构前行星架45传递到机械传动机构后行星架47，两路机械功率流经机械传动机构后齿圈49汇合后，经机械传动机构输出轴411和功率汇流机构5，从输出轴6输出。此时，输出转速与输入转速关系为：
n o＝0.5n I。
F 2(M)档位功率流向如图13所示。当接合离合器C 2 32、离合器C 3 42和离合器C 4 55时，功率分流机构3、机械传动机构4和功率汇流机构5各自固连为一体，主离合器C 1 2接合后传递的发动机动力，经功率分流机构3、机械传动机构4和功率汇流机构5，从输出轴6输出。此时，输出转速与输入转速关系为：
n o＝n I。
表1各元件接合表
Figure PCTCN2020106687-appb-000009
Figure PCTCN2020106687-appb-000010
注：“▲”代表元件处于接合状态；
主要参数：n o为输出轴转速，n e为发动机转速，e为液压传动机构的排量比，i为相关齿轮传动比，k s为功率分流行星齿轮特性参数，k v为功率汇流行星齿轮特性参数，k f为前行星齿轮机构特性参数，k r为后行星齿轮机构特性参数；i 1i 2＝1.0，k s＝3.5，k v＝3.5，k f＝1.8，k r＝2.5。
“F”代表前进方向，“R”代表后退方向，“H”代表液压传动，“M”代表机械传动，“HM”代表机液传动，“HMs”代表功率分流机液传动，“HMv”代表功率汇流机液传动。
本发明的调速特性曲线如图14所示。当e∈(0，1.00)范围内，R(H)档位的调速范围为n o∈(-0.78，0)n I，F 1(H)档位的调速范围为n o∈(0，0.22)n I，F 2(H)档位的调速范围为n o∈(0，1.00)n I；当e∈(0,1.00)范围内，R(HMs)档位调速范围为n o∈(-0.29，0)n I；当e∈(0.25,1.00)范围内，F 1(HMs)档位调速范围为n o∈(0.44，0.70)n I，F 2(HMs)档位调速范围为n o∈(1.00，7.00)n I；当e∈(0,1.00)范围内，R(HMs)档位调速范围为n o∈(-0.31，-0.09)n I，F 1(HMs)档位调速范围为n o∈(0.39，0.61)n I，F 2(HMs)档位调速范围为n o∈(0.78，1.00)n I；R(M)、F 1(M)和F 2(M)的调速值分别为n o＝-0.4n I、n o＝0.5n I和n o＝n I。
可由两种液压启动方式，如图14(a)所示。当e＝0.50时，F 2(H)档位可无动力中断切换到F 1(HMs)档位；当e＝1.00时，F 2(H)档位可无动力中断切换到F 2(HMs)档位；此时非线性调速，如图14(b)所示。当e＝0.50时，F 2(H)档位可无动力中断切换到F 1(HMv)档位；当e＝1.00时，F 2(H)档位可无动力中断切换到F 2(HMv)档位；此时线性调速，如图14(c)所示。当e＝0.31时，R(H)档位可无动力中断切换到R(HMs)档位或R(HMv)档位，如图14(d)所示。
进一步分析可知，F 2(H)、F 1(HMs)和F 1(HMv)在e＝0.50时可无动力中断换挡，F 2(H)、F 2(HMs)和F 2(HMv)在e＝1.00时可无动力中断换挡，即以上各档位间可实现无级调速。
传动装置正向传动时，液压传动采用两个正向档位，F 1(H)档位主要采用低速大转矩满足动力性要求较高的工况，F 2(H)档位既可用于连接功率分流机液传动的F 1(HMs)档位和F 2(HMs)档位，也可用于连接功率汇流机液传动的F 1(HMv)档位和F 2(HMv)档位，实现无级调速。所述F 2(H)档位、F 1(HMs)档位、F 2(HMs)档位、F 1(HMv)档位和F 2(HMv)档位之间，可通过调节液压传动机构7的传动比和选择性控制所述离合器C 1(2)、离合器C 2 32、离合器C 3 42、离合器C 4 55、离合器C 5 71、离合器C 6 77、制动器B 1 46和制动器B 2 43的接合，实现无级调速。
传动装置正向传动时，液压传动采用R(H)档位连接功率分流机液传动的R(HMs)档位和功率汇流机液传动的R(HMv)档位，实现无级调速。所述R(H)档位、R(HMs)档位和R(HMv)档位之间，可通过调节液压传动机构7的传动比和选择性控制所述离合器C 1 2、离合器C 2 32、离合器C 3 42、离合器C 4 55、离合器C 5 71、离合器C 6 77、制动器B 1 46和制动器B 2 43的接合，实现无级调速。
所述实施例为本发明的优选的实施方式，但本发明并不限于上述实施方式，在不背离本发明的实质内容的情况下，本领域技术人员能够做出的任何显而易见的改进、替换或变型均属于本发明的保护范围。

Claims (10)

  1. 一种功率分流和功率汇流相结合的机液复合传动装置，其特征在于，包括输入构件、功率分流机构(3)、机械传动机构(4)、功率汇流机构(5)、输出构件、液压传动机构(7)、离合器组件和制动器组件；所述输入构件与功率分流机构(3)连接，所述功率汇流机构(5)与输出构件连接，所述离合器组件将所述功率分流机构(3)的输出端分别连接到机械传动机构(4)的输入端和液压传动机构(7)的输入端，将所述功率汇流机构(5)的输入端分别连接到机械传动机构(4)的输出端和液压传动机构(7)的输出端；所述离合器组件和制动器组件提供输入构件与输出构件之间连续的传动比。
  2. 根据权利要求1所述的功率分流和功率汇流相结合的机液复合传动装置，其特征在于，通过调节液压传动机构(7)的排量比和选择性控制所述离合器组件和制动器组件的接合，提供输入构件与输出构件之间的传动方式包括：液压传动、功率分流机液传动、功率汇流机液传动和机械传动。
  3. 根据权利要求2所述的功率分流和功率汇流相结合的机液复合传动装置，其特征在于，所述机械传动机构(4)包括机械传动机构输入轴(41)、前行星齿轮机构和后行星齿轮机构，所述后行星齿轮机构的太阳轮和前行星齿轮机构的齿圈分别与机械传动机构输入轴(41)连接；所述前行星齿轮机构的行星架和后行星齿轮机构的行星架连接；
    所述功率分流机构(3)包括功率分流行星轮机构，所述功率分流行星轮机构的齿圈与输入构件连接，所述功率分流行星轮机构的太阳轮与液压传动机构(7)的输入端连接，所述功率分流行星轮机构的行星架与机械传动机构输入轴(41)连接；
    所述功率汇流机构(5)包括功率汇流行星轮机构，所述后行星齿轮机构的齿圈与功率汇流行星轮机构的齿圈连接；所述功率汇流行星轮机构的行星架与输出构件连接，所述功率汇流行星轮机构的太阳轮与液压传动机构(7)的输出端连接。
  4. 根据权利要求3所述的功率分流和功率汇流相结合的机液复合传动装置，其特征在于，所述离合器组件包括离合器C 2(32)、离合器C 4(55)、离合器C 5(71)和离合器C 6(77)；所述离合器C 2(32)选择性的将功率分流行星轮机构的齿圈与功率分流行星轮机构的行星架连接以共同旋转；所述离合器C 4(55)选择性的将功率汇流行星轮机构的齿圈与功率汇流行星轮机构的行星架连接以共同旋转；所述离合器C 5(71)选择性的将功率分流行星轮机构的太阳轮与液压传动机构(7)的输入端连接以共同旋转；所述离合器C 6(77)选择性的将液压传动机构(7)的输出端与功率汇流行星轮机构的太阳轮连接以共同旋转；所述制动器组件包括制动器B 1(46)、制动器B 2(43)和制动器B 3(51)，所述制动器B 1(46)用于选择性的将前行星齿轮机构的行星架连接到固定件；所述制动器B 2(43)用于选择性的将前行星齿轮机构的太阳轮连接到固定件；所述制动器B 3(51)用于选择性的将功率汇流行星轮机构的 齿圈连接到固定件；通过调节液压传动机构(7)的排量比和选择性控制所述离合器C 2(32)、离合器C 4(55)、离合器C 5(71)、离合器C 6(77)、制动器B 1(46)、制动器B 2(43)和制动器B 3(51)的接合，提供输入构件与输出构件之间的连续前进或后退的液压传动。
  5. 根据权利要求4所述的功率分流和功率汇流相结合的机液复合传动装置，其特征在于，接合所述离合器C 5(71)、离合器C 6(77)、制动器B 1(46)和制动器B 2(43)，提供输入构件与输出构件之间后退方向的液压传动；
    接合所述离合器C 5(71)、离合器C 6(77)、离合器C 2(32)和制动器B 3(51)，接合所述离合器C 5(71)、离合器C 6(77)、离合器C 2(32)和离合器C 4(55)，分别提供输入构件与输出构件之间前进方向各自相异的液压传动。
  6. 根据权利要求4所述的功率分流和功率汇流相结合的机液复合传动装置，其特征在于，所述离合器组件还包括离合器C 3(42)，所述离合器C 3(42)选择性的将前行星齿轮机构的齿圈与前行星齿轮机构的太阳轮连接以共同旋转；
    接合所述离合器C 4(55)、离合器C 5(71)、离合器C 6(77)和制动器B 1(46)提供输入构件与输出构件之间后退方向的功率分流机液传动；
    接合所述离合器C 4(55)、离合器C 5(71)、离合器C 6(77)和制动器B 2(43)，接合所述离合器C 3(42)、离合器C 4(55)、离合器C 5(71)和离合器C 6(77)，分别提供输入构件与输出构件之间前进方向各自相异的功率分流机液传动。
  7. 根据权利要求6所述的功率分流和功率汇流相结合的机液复合传动装置，其特征在于，接合所述离合器C 2(32)、离合器C 5(71)、离合器C 6(77)和制动器B 1(46)提供输入构件与输出构件之间后退方向的功率汇流机液传动；
    接合所述离合器C 2(32)、离合器C 5(71)、离合器C 6(77)和制动器B 2(43)，接合所述离合器C 2(32)、离合器C 3(42)、离合器C 5(71)和离合器C 6(77)，分别提供输入构件与输出构件之间前进方向各自相异的功率汇流机液传动。
  8. 根据权利要求6所述的功率分流和功率汇流相结合的机液复合传动装置，其特征在于，接合所述离合器C 2(32)、离合器C 4(55)和制动器B 1(46)，提供输入构件与输出构件之间后退方向的机械传动；
    接合所述离合器C 2(32)、离合器C 4(55)和制动器B 2(43)，接合所述离合器C 2(32)、离合器C 3(42)和离合器C 4(55)，分别提供输入构件与输出构件之间前进方向各自相异的机械传动。
  9. 根据权利要求6所述的功率分流和功率汇流相结合的机液复合传动装置，其特征在于，通过调节液压传动机构7的排量比和选择性控制所述离合器C 1(2)、离合器C 2(32)、离合 器C 3(42)、离合器C 4(55)、离合器C 5(71)、离合器C 6(77)、制动器B 1(46)和制动器B 2(43)的接合，提供前进方向的液压传动分别与前进方向的功率分流机液传动和前进方向的功率汇流机液传动之间的无级调速。
  10. 根据权利要求6所述的功率分流和功率汇流相结合的机液复合传动装置，其特征在于，通过调节液压传动机构7的排量比和选择性控制所述离合器C 1(2)、离合器C 2(32)、离合器C 3(42)、离合器C 4(55)、离合器C 5(71)、离合器C 6(77)、制动器B 1(46)和制动器B 2(43)的接合，提供后退方向的液压传动分别与后退方向的功率分流机液传动和后退方向的功率汇流机液传动之间的无级调速。
PCT/CN2020/106687 2020-07-20 2020-08-04 一种功率分流和功率汇流相结合的机液复合传动装置 Ceased WO2022016607A1 (zh)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118775510A (zh) * 2024-07-18 2024-10-15 南京林业大学 一种换挡时双流同步传动的单流输出并联多模式无级变速器及其换挡控制方法

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113137462B (zh) * 2021-05-18 2022-05-03 吉林大学 一种作业车辆的行走传动装置及其控制方法
CN113147378B (zh) * 2021-05-18 2022-10-04 吉林大学 一种多模式机械液压传动装置及其控制方法
CN114607746B (zh) * 2022-02-17 2025-02-14 江苏大学 一种液压机械串并联共存的传动装置及其控制方法
GB2614160B (en) 2022-02-22 2024-11-06 Univ Jiangsu Multi-mode hydro-mechanical hybrid transmission device
CN115076327B (zh) * 2022-02-22 2025-05-06 江苏大学 一种多模式机液复合传动装置
CN114593180B (zh) * 2022-02-25 2025-02-18 江苏大学 一种机械与电气无级变速的复合传动系统及其控制方法
CN114688227B (zh) * 2022-04-21 2023-01-24 扬州大学 一种液压、锥齿及齿轮多模式传动装置
US12379026B2 (en) 2022-06-07 2025-08-05 Jiangsu University Mechanical-electrical-hydraulic hybrid transmission device and control method thereof
CN114909453B (zh) * 2022-06-07 2023-08-22 江苏大学 一种机电液复合传动装置及其控制方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008082540A (ja) * 2006-08-28 2008-04-10 Denso Corp 油圧制御装置
CN110822053A (zh) * 2019-10-08 2020-02-21 江苏大学 一种多功率分配模式的机械液压复合传动装置及控制方法
CN110953318A (zh) * 2019-11-06 2020-04-03 江苏大学 一种机械液压复合传动装置及控制方法

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3147447C2 (de) * 1981-12-01 1984-06-14 Jarchow, Friedrich, Prof. Dr.-Ing., 4300 Essen Hydrostatischmechanisches Stellkoppelgetriebe mit eingangsseitiger Leistungsverzweigung
US5277670A (en) * 1988-03-30 1994-01-11 Zahnradfabrik Friedrichshafen, Ag. Circuit change-over gear with infinitely variable transmission
CN107859723B (zh) * 2017-11-21 2019-05-21 河南科技大学 一种多模式液压机械无级变速装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008082540A (ja) * 2006-08-28 2008-04-10 Denso Corp 油圧制御装置
CN110822053A (zh) * 2019-10-08 2020-02-21 江苏大学 一种多功率分配模式的机械液压复合传动装置及控制方法
CN110953318A (zh) * 2019-11-06 2020-04-03 江苏大学 一种机械液压复合传动装置及控制方法

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118775510A (zh) * 2024-07-18 2024-10-15 南京林业大学 一种换挡时双流同步传动的单流输出并联多模式无级变速器及其换挡控制方法

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