WO2022016608A1 - 一种具有自动调节功能的功率分流式机液复合传动系统 - Google Patents

一种具有自动调节功能的功率分流式机液复合传动系统 Download PDF

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Publication number
WO2022016608A1
WO2022016608A1 PCT/CN2020/106688 CN2020106688W WO2022016608A1 WO 2022016608 A1 WO2022016608 A1 WO 2022016608A1 CN 2020106688 W CN2020106688 W CN 2020106688W WO 2022016608 A1 WO2022016608 A1 WO 2022016608A1
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Prior art keywords
clutch
hydraulic
pump
transmission
confluence
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Ceased
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PCT/CN2020/106688
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English (en)
French (fr)
Inventor
蔡英凤
朱镇
陈龙
王骏骋
夏长高
韩江义
徐兴
施德华
窦磊
汪佳佳
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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 US17/430,733 priority Critical patent/US11313447B1/en
Priority to CH70282/21A priority patent/CH717778B1/de
Priority to GB2111719.7A priority patent/GB2597849B/en
Priority to DE112020000862.2T priority patent/DE112020000862T5/de
Publication of WO2022016608A1 publication Critical patent/WO2022016608A1/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
    • 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
    • F16H61/0009—Hydraulic control units for transmission control, e.g. assembly of valve plates or valve units
    • 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
    • F16H61/0021—Generation or control of line pressure
    • F16H61/0025—Supply of control fluid; Pumps therefor
    • F16H2061/0034—Accumulators for fluid pressure supply; Control thereof
    • 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
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
    • F16H2200/2051—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eight engaging means

Definitions

  • the invention relates to the field of vehicle gearboxes, in particular to a power-splitting machine-hydraulic composite transmission system with automatic adjustment function.
  • Hydraulic-mechanical composite transmission adopts hydraulic transmission to realize starting working condition, machine-hydraulic transmission realizes working working condition, and mechanical transmission realizes transition working condition, adapting to different working conditions.
  • the power split mode adopts 2K-H planetary gear mechanism in front, which is mainly suitable for low-power transmission systems;
  • the power confluence mode adopts 2K-H planetary gear mechanism in the rear, which is mainly suitable for high-power transmission systems.
  • the traditional hydraulic speed regulation mainly adopts the volume speed regulation method, and the speed regulation is carried out by controlling the displacement of the variable pump. It is difficult for the engine as the power source to meet the requirements of its power and fuel economy. It is difficult to meet the traction power requirements of the high-power transmission system represented by the power split method, but it is one of the feasible solutions to improve the performance of the low-power transmission system represented by the power split method.
  • the safety and reliability performance and energy saving and emission reduction characteristics of the vehicle transmission system are the current research hotspots, but they are not widely used in the mechanical-hydraulic composite transmission.
  • the hydraulic transmission mechanism integrating safety, reliability and energy utilization can greatly improve the performance of the mechanical-hydraulic composite transmission system. performance.
  • the present invention provides a power-splitting machine-hydraulic compound transmission system with automatic adjustment function, capable of multi-mode stepless speed change, and functions of energy reuse and emergency guarantee.
  • the present invention achieves the above technical purpose through the following technical means.
  • a power shunt machine-hydraulic composite transmission system with automatic adjustment function comprising an input member, a hydraulic transmission mechanism, a shunt mechanism, a confluence mechanism, an output member, a clutch assembly and a brake assembly; the clutch assembly connects the input member and the shunt mechanism.
  • the input end is connected, and the output end of the shunt mechanism is respectively connected to the input end of the hydraulic transmission mechanism and the input end of the confluence mechanism, and the output end of the hydraulic transmission mechanism is connected with the output member; the output end of the confluence mechanism is connected with the output member;
  • the clutch and brake assemblies provide a continuous gear ratio between the input member and the output member.
  • the transmission modes provided between the input mechanism and the output member include hydraulic transmission, hydraulic transmission and mechanical transmission.
  • the shunt mechanism includes a shunt mechanism ring gear, a shunt mechanism planet carrier and a shunt mechanism sun gear; the shunt mechanism ring gear is connected to the input member;
  • the confluence mechanism includes a common ring gear of the confluence mechanism, a small sun gear of the confluence mechanism, a large sun gear of the confluence mechanism, a short planet carrier of the confluence mechanism and a long planet carrier of the confluence mechanism; the short planet carrier of the confluence mechanism is connected to the long planet carrier of the confluence mechanism, The long planet carrier of the confluence mechanism is connected to the output member; the common ring gear of the confluence mechanism, the small sun gear of the confluence mechanism and the short planetary carrier of the confluence mechanism form a planetary gear train, the common ring gear of the confluence mechanism, the large sun gear of the confluence mechanism It forms another planetary gear train with the long planetary carrier of the confluence mechanism;
  • the clutch assembly includes a clutch C 1 and a clutch C 2 , the clutch C 1 is used for selectively connecting the sun gear of the split mechanism with the input end of the hydraulic transmission mechanism for common rotation; the clutch C 2 is used for selectively the output of the output member of the hydraulic actuators connected for common rotation; said brake assembly comprising a brake B 1, B of the brake mechanism of the shunt is connected to the carrier for selectively fixing member 1;
  • Engagement of the clutch C 1 , clutch C 2 and brake B 1 provides hydraulic transmission between the input member and the output member to advance or reverse.
  • the clutch assembly further includes a clutch C 3 , a clutch C 4 and a clutch C 5 ;
  • the clutch C 3 is used to selectively connect the planet carrier of the split mechanism with the large sun gear of the confluence mechanism for common rotation;
  • the clutch C 4 is used to selectively connect the small sun gear of the confluence mechanism with the large sun gear of the confluence mechanism for common rotation;
  • the clutch C 5 is used to selectively connect the splitter mechanism ring gear with the splitter mechanism planet carrier for common rotation;
  • the brake assembly further includes a brake B 2 and a brake B 3 , the brake B 2 is used for selectively connecting the small sun gear of the confluence mechanism to the fixed part;
  • the brake B 3 is used for selectively connecting the common ring gear of the confluence mechanism to the fixture;
  • the clutch C 4 and the clutch C 5 respectively provide mechanical transmission with different forward directions between the input member and the output member.
  • Engaging the clutch C 1 , clutch C 2 , clutch C 3 and brake B 2 , or engaging the clutch C 1 , clutch C 2 , clutch C 3 and clutch C 4 , respectively, provides a forward direction between the input and output members Different hydraulic transmissions.
  • the hydraulic transmission mechanism includes a variable pump, an oil replenishment system, an electromagnetic reversing valve V 3 , a proportional throttle valve V 8 , a safety valve group, a three-position four-way proportional directional valve V 9 , a high-pressure accumulator A 1 , Low pressure accumulator A 2 , emergency valve V 10 , and pump/motor mechanism, the input of the variable pump is connected to the output of the shunt mechanism through clutch C 1 , and the output of the pump/motor mechanism is connected to the output through clutch C 2
  • the components are connected, the variable pump is used to drive the pump/motor mechanism, and the high-pressure hydraulic pipeline between the outlet of the variable pump and the inlet of the pump/motor mechanism is provided with an electromagnetic reversing valve V 3 for one-way oil flow; the low-pressure hydraulic pipeline between the inlet of the variable pump and the outlet of the pump/motor mechanism is provided with a proportional throttle valve V 8 ; a proportional directional valve V 9 is connected in parallel between the low-pressure hydraulic pipeline and
  • the low-pressure hydraulic pipeline and the high-pressure hydraulic pipeline are respectively provided with safety valve groups for adjusting the pipeline pressure; the oil replenishing system is used to supplement the hydraulic oil in the low-pressure hydraulic pipeline and/or the high-pressure hydraulic pipeline.
  • the clutch C 2 is engaged, so that the braking energy of the output member is transmitted to the pump/motor mechanism; the pump/motor mechanism is in the hydraulic pump condition; the electromagnetic reversing valve V is controlled 3 is energized, so that the oil will not be back to a variable pump; V 8 controls the throttle valve opening ratio decreases, to increase for the pump / motor pressure oil outlet means; controlling the proportional directional valve V 9 to make a 2 of the low-pressure accumulator in communication with the intake port of the pump / motor mechanism, for the oil supplement; the proportional directional control valve V 9 so that the high pressure accumulator oil a 1 and pump / motor mechanism The mouth is connected to store energy.
  • the pump / motor means is a hydraulic pump condition; controlling the energization of the solenoid valve V 3, so that the oil will not be back to a variable pump; controlling the proportional directional valve V 9 Connect the low-pressure accumulator A 2 with the oil outlet of the pump/motor mechanism; control the proportional directional valve V 9 to make the high-pressure accumulator A 1 communicate with the oil inlet of the pump/motor mechanism; the A 1 alone high pressure accumulator the high pressure accumulator or the pump A 1 and the common variable driving the pump / motor mechanism; A 2 of said low pressure accumulator for recovering residual energy.
  • low pressure emergency valve V 10 is also connected in parallel between the high-pressure hydraulic line and the hydraulic pipes; control valve V 10 for the emergency power-off outside the pump variable transmission, or switching power pump / motor internal storage mechanism, or Release the power stored in the high pressure accumulator A 1 and the low pressure accumulator A 2.
  • the power-splitting machine-hydraulic composite transmission system with automatic adjustment function of the present invention adopts hydraulic transmission, machine-hydraulic transmission and mechanical transmission to adapt to different operating conditions.
  • the power shunt machine-liquid composite transmission system with automatic adjustment function of the present invention can adjust the displacement ratio of the hydraulic transmission mechanism by controlling the displacement of the variable pump, control the frequency converter to control the speed of the motor, switch the corresponding clutch components and Brake assembly, various transmission modes to improve forward and reverse gears.
  • the power shunt machine-liquid composite transmission system with automatic adjustment function combines the main power source composed of various valves, frequency converters and electric motors, the auxiliary power source composed of accumulator, and the variable pump, Provides a high reliability and multi-degree-of-freedom transmission system.
  • FIG. 1 is a schematic diagram of the power-splitting machine-hydraulic composite transmission system with automatic adjustment function according to the present invention.
  • FIG. 2 is a schematic diagram of the power flow of the F(H)/R(H) gear of the present invention.
  • FIG. 3 is a schematic diagram of the power flow of the R(M) gear according to the present invention.
  • FIG. 4 is a schematic diagram of the power flow of the F 1 (M) gear of the present invention.
  • FIG. 5 is a schematic diagram of the power flow of the F 2 (M) gear of the present invention.
  • FIG. 6 is a schematic diagram of the power flow of the R(HM) gear according to the present invention.
  • FIG. 7 is a schematic diagram of the power flow of the F 1 (HM) gear of the present invention.
  • FIG. 8 is a schematic diagram of the power flow of the F 2 (HM) gear according to the present invention.
  • FIG. 9 is a schematic diagram of the auxiliary power source energy recovery of the present invention.
  • FIG. 10 is a schematic diagram of the auxiliary power source and the electric motor jointly driving the transmission device of the present invention.
  • FIG. 11 is a schematic diagram of the power release flow of the pump/motor mechanism of the present invention.
  • FIG. 12 is a schematic diagram of the power release flow of the variable pump of the present invention.
  • FIG. 13 is a schematic diagram of the power release flow of the auxiliary power source of the present invention.
  • the power shunt machine-liquid composite transmission system with automatic adjustment function includes a frequency converter 1, a motor 2, an input shaft 3, a hydraulic transmission mechanism 4, a shunt mechanism 5, and a mechanical transmission mechanism 6 , a confluence mechanism 7 and an output shaft 8; the frequency converter 1 drives the input shaft 3 to rotate through the motor 2.
  • the shunt 5 includes a clutch mechanism C 5 51, splitter gear mechanism 52, the carrier distribution means 53 and the sun gear 54 split mechanism; the clutch C 5 51 52 for connecting the distribution means and the distribution means is a ring gear carrier 53, The shunt mechanism ring gear 52 is fixedly connected with the input shaft 3, the shunt mechanism sun gear 54 is connected with the input end of the hydraulic transmission mechanism 4, and the shunt mechanism planet carrier 53 is connected with the mechanical transmission mechanism 6;
  • the mechanical transmission mechanism 6 includes a brake B 1 61, a mechanical transmission shaft 62 and a clutch C 3 63; the mechanical transmission shaft 62 is used to connect the split mechanism 5 and the confluence mechanism 7, and the brake B 1 61 is used to brake the mechanical transmission shaft 62, the clutch C 3 63 is used to connect the mechanical transmission shaft 62;
  • the confluence mechanism 7 includes a brake B 2 71 , a clutch C 4 72 , a brake B 3 73 , the confluence mechanism common ring gear 74 , the confluence mechanism small sun gear 75 , the confluence mechanism large sun gear 76 , the confluence mechanism short planet carrier 77 and the confluence mechanism.
  • the long planet carrier 78 of the mechanism; the large sun gear 76 of the confluence mechanism is connected with the mechanical transmission shaft 62, the short planet carrier 77 of the confluence mechanism and the long planet carrier 78 of the confluence mechanism are fixedly connected with the output shaft 8, and the clutch C 4 72 is used for connection
  • the small sun gear 75 of the confluence mechanism and the mechanical transmission shaft 62, the brake B 2 71 is used to brake the small sun gear 75 of the confluence mechanism, and the brake B 3 73 is used to brake the common ring gear 74 of the confluence mechanism.
  • the hydraulic transmission mechanism 4 includes a hydraulic transmission input gear pair 41, a clutch C 1 42, a variable pump shaft 43, a variable pump 44, an oil charge pump 45, an electromagnetic reversing valve V 3 46, a proportional throttle valve V 8 47, a pilot proportional Relief valve V 7 48, pilot proportional relief valve V 6 49, proportional directional valve V 9 410, high pressure accumulator A 1 411, low pressure accumulator A 2 412, emergency valve V 10 413, pump/motor mechanism 414 , pump motor mechanism shaft 415, hydraulic transmission output gear pair 416 and clutch C 2 417;
  • the pump/motor mechanism 414 is a device that can switch functions between the hydraulic pump and the hydraulic motor, that is, when the pump/motor mechanism 414 inputs For mechanical energy, the pump/motor mechanism 414 outputs hydraulic energy, and when the pump/motor mechanism 414 inputs hydraulic energy, the pump/motor mechanism 414 outputs mechanical energy.
  • the clutch C 1 42 connects the shunt mechanism 5 and the variable displacement pump shaft 43 through the hydraulic transmission input gear pair 41, and the clutch C 2 417 connects the confluence mechanism 7 and the pump/motor mechanism shaft 415 through the hydraulic transmission output gear pair 416;
  • the variable displacement pump 44 drives the pump/motor mechanism 414;
  • an electromagnetic reversing valve V 3 46 is provided between the variable pump 44 and the high-pressure hydraulic pipeline of the pump/motor mechanism 414 for one-way flow of oil;
  • the variable pump 44 and A proportional throttle valve V 8 47 is provided between the low-pressure hydraulic pipes of the pump/motor mechanism 414;
  • a three-position four-way proportional parallel connection is provided between the variable pump 44 and the high and low-pressure hydraulic pipes of the pump/motor mechanism 414
  • Directional valve V 9 410 and emergency valve V 10 413, three-position four-way proportional directional valve V 9 410, the upper and lower valve ports on the left side are respectively connected to high and low pressure pipelines, and the upper and lower valve ports on
  • the low-pressure hydraulic pipeline and the high-pressure hydraulic pipeline are respectively provided with safety valve groups to adjust the pipeline pressure;
  • the safety valve group includes two one-way valves, a pilot proportional relief valve V 7 48 and a pilot proportional relief valve V 6 49.
  • the two check valves are connected in parallel between the low-pressure hydraulic pipeline and the high-pressure hydraulic pipeline after being backed in series;
  • the pilot proportional relief valve V 7 48 and the pilot proportional relief valve V 6 49 are connected in series and then connected in parallel between the low-pressure hydraulic pipeline and the high-pressure hydraulic pipeline.
  • a communication branch is provided between the high-pressure hydraulic pipelines; between the two one-way valves, and between the pilot proportional relief valve V 7 48 and the pilot proportional relief valve V 6 49 .
  • the oil replenishment system is used to supplement the hydraulic oil in the low pressure hydraulic pipeline and/or the high pressure hydraulic pipeline.
  • the oil charge system includes a charge oil pump 45 , a relief valve V 1 and a check valve V 2 .
  • the outlet end of the oil charging system communicates with the branch.
  • the transmission modes provided between the input mechanism and the output member include: hydraulic transmission, machine-hydraulic transmission and Mechanical transmission.
  • Hydraulic transmission includes R(H) gear and F(H) gear, as follows:
  • n E is the motor speed
  • n o is the output speed
  • e is the displacement ratio of the hydraulic transmission mechanism.
  • 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 3.
  • the clutch C 3 63, the clutch C 5 51 and the brake B 3 73 are engaged, the power output by the inverter 1 to drive the motor 2 passes through the input shaft 3, the shunt mechanism 5, the mechanical transmission mechanism 6, and the confluence mechanism that are firmly connected as a whole.
  • the sun gear 76 and the long carrier 78 of the confluence mechanism are output from the output shaft 8 .
  • the relationship between the output speed and the input speed is:
  • the power flow of the F 1 (M) gear is shown in Figure 4.
  • the clutch C 3 63, the clutch C 5 51 and the brake B 2 71 are engaged, the power output by the inverter 1 to drive the electric motor 2 passes through the input shaft 3, the shunt mechanism 5, the mechanical transmission mechanism 6, and the confluence mechanism that are fixed as a whole.
  • the sun gear 76 , the common ring gear 74 of the confluence mechanism, and the long carrier 78 of the confluence mechanism are output from the output shaft 8 .
  • the relationship between the output speed and the input speed is:
  • the power flow of the F 2 (M) gear is shown in Figure 5.
  • the clutch C 3 63, the clutch C 4 72 and the clutch C 5 51 are engaged, the power output by the inverter 1 to drive the motor 2 passes through the input shaft 3, the shunt mechanism 5, the mechanical transmission mechanism 6, and the fixed connection as a whole.
  • the integrated manifold 7 is output from the output shaft 8 .
  • the relationship between the output speed and the input speed is:
  • n o n E .
  • the mechanical transmission includes R (HM), F 1 (HM) and F 2 (HM), as follows:
  • the power flow of the R(HM) gear is shown in Figure 6.
  • the clutch C 1 42, the clutch C 2 417, the clutch C 3 63 and the brake B 3 73 are engaged, the power output by the inverter 1 to drive the motor 2 is divided into two paths through the input shaft 3 and the gear ring gear 52 of the shunt mechanism.
  • the shunt mechanism planet carrier 53, the mechanical transmission shaft 62 and the large sun gear 76 of the confluence mechanism are transmitted to the long planet carrier 78 of the confluence mechanism, all the way through the sun gear 54 of the shunt mechanism and the hydraulic transmission mechanism 4, to the long planet carrier 78 of the confluence mechanism, and mixed
  • the power is combined by the long planet carrier 78 of the confluence mechanism, and is output from the output shaft 8 .
  • the relationship between the output speed and the input speed is:
  • the power flow of the F 1 (HM) gear is shown in Figure 7.
  • the clutch C 1 42, the clutch C 2 417, the clutch C 3 63 and the brake B 2 71 are engaged, the power output by the inverter 1 to drive the motor 2 is divided into two paths through the input shaft 3 and the gear ring gear 52 of the shunt mechanism.
  • the planet carrier 53 of the shunt mechanism, the mechanical transmission shaft 62, the large sun gear 76 of the confluence mechanism and the common ring gear 74 of the confluence mechanism are transmitted to the long planet carrier 78 of the confluence mechanism, and all the way through the sun gear 54 of the shunt mechanism and the hydraulic transmission mechanism 4, and transmitted to the confluence mechanism
  • the long planetary carrier 78 of the mechanism, the hybrid power is merged through the long planetary carrier 78 of the confluence mechanism, and is output from the output shaft 8 .
  • the relationship between the output speed and the input speed is:
  • the power flow of the F 2 (HM) gear is shown in Figure 8.
  • the clutch C 1 42, the clutch C 2 417, the clutch C 3 63 and the clutch C 4 72 are engaged, the power output by the inverter 1 to drive the motor 2 is divided into two paths through the input shaft 3 and the gear ring gear 52 of the shunt mechanism.
  • the shunt mechanism planet carrier 53 and the mechanical transmission shaft 62 are transmitted to the confluence mechanism 7 that is fixed as one, and all the way through the sun gear 54 of the shunt mechanism and the hydraulic transmission mechanism 4, and are transmitted to the confluence mechanism 7 that is fixed as a whole, and the hybrid power is output from the output Axis 8 output.
  • the relationship between the output speed and the input speed is:
  • n o is the output shaft rotational speed
  • n E is the motor speed
  • e is the displacement of the hydraulic transmission ratio
  • i is the gear ratio of the associated gear
  • Various transmission modes on the premise that the displacement ratio of the hydraulic transmission mechanism remains unchanged, can be adjusted steplessly by adjusting the speed of the motor, and the direction of the output shaft speed is determined by the direction of the motor speed.
  • the displacement ratio of the hydraulic transmission mechanism can also be controlled by adjusting the displacement of the variable pump, and the speed of the motor can be adjusted by controlling the frequency converter.
  • the displacement ratio range of the hydraulic transmission mechanism is: e ⁇ [0,1].
  • the speed regulation range of the F(H) gear is n 0 ⁇ [0,n Emax ]; when the motor steering is negative, the speed regulation range of the R(H) gear is n 0 ⁇ [-n Emax ,0].
  • the speed regulation range of R(M) gear is: n 0 ⁇ [-0.55n Emax ,0];
  • the speed regulation range of F 1 (M) gear is: n 0 ⁇ [0,0.55n Emax ];
  • the speed regulation range of F 2 (M) gear is: n 0 ⁇ [0,n Emax ];
  • the speed regulation range of R(HM) gear is: n 0 ⁇ [-0.27n Emax ,0];
  • the F 1 (HM) gear and the F 2 (HM) gear can be obtained by switching the F (H) gear, and the value range of the displacement ratio of the two-speed hydraulic transmission mechanism is: e ⁇ [0.50,1.00] ;
  • the F(H) gear and the F 2 (HM) gear can be shifted synchronously.
  • the value range of the F 2 (HM) gear is: n 0 ⁇ [0,3n Emax ].
  • 1R (H) gear is realized by the reverse rotation of the motor and the adjustment of the displacement ratio of the hydraulic transmission mechanism, and the speed regulation range is n 0 ⁇ [-n Emax ,0];
  • 2R(M) gear is realized by the forward rotation of the motor, and the speed regulation range is n 0 ⁇ [-0.55n Emax ,0];
  • the R(HM) gear is realized by the forward rotation of the motor and the adjustment of the displacement ratio of the hydraulic transmission mechanism.
  • the speed regulation range is n 0 ⁇ [-0.27n Emax ,0].
  • the forward drive of the system can be realized in five ways:
  • the F(H) gear is realized by the forward rotation of the motor and the adjustment of the displacement ratio of the hydraulic transmission mechanism, and the speed regulation range is n 0 ⁇ [0,n Emax ];
  • 5F 1 (M) gear is realized by the forward rotation of the motor, and the speed regulation range is n 0 ⁇ [0,0.55n Emax ];
  • 6F 2 (M) gear is realized by the forward rotation of the motor, and the speed regulation range is n 0 ⁇ [0,n Emax ];
  • the oil outlet of the pump/motor mechanism 414 When the pressure at the oil outlet of the pump/motor mechanism 414 is greater than the set pressure of the high pressure accumulator A 1 411, the oil outlet of the pump/motor mechanism 414 stores energy in the high pressure accumulator A 1 411, and the low pressure accumulator A 2 412 The oil inlet of the pump/motor mechanism 414 may be replenished with oil.
  • the pump/motor mechanism 414 when the vehicle is accelerating, the pump/motor mechanism 414 is in the hydraulic motor condition, and the electromagnetic reversing valve V 3 46 is energized to ensure that the external oil will not flow back to the variable pump 44, and the three-position four-way proportional direction
  • the valve V 9 410 is in the upper position, and the pilot proportional relief valve V 6 49 adjusts the safety pressure of the system and ensures the realization of the oil discharge process.
  • the high pressure accumulator A 1 411 alone or together with the variable displacement pump 44 releases energy to drive the pump/motor mechanism 414 to operate, and the low pressure accumulator A 2 412 can recover the remaining energy.
  • the electromagnetic reversing valve V 3 46 is energized to ensure that the external oil will not flow back to the variable pump 44 , the emergency valve V 10 413 is energized, and the pump/motor mechanism 414 is energized.
  • the pressure at the oil inlet and the oil outlet are equal, and the braking energy cannot be further stored in the energy storage mechanism or transmitted to the variable displacement pump 44 .
  • the electromagnetic reversing valve V 3 46 is energized to ensure that the external oil will not flow back to the variable pump 44, the emergency valve V 10 413 is energized, the high-pressure accumulator A 1 411 and the low-pressure accumulator A 2 412 are connected, The last two accumulators have the same pressure.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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Abstract

本发明提供了一种具有自动调节功能的功率分流式机液复合传动系统，包括输入构件、液压传动机构、分流机构、汇流机构、输出构件、离合器组件和制动器组件；所述离合器组件将输入构件与分流机构的输入端连接，将分流机构的输出端分别连接到液压传动机构的输入端和汇流机构的输入端，将液压传动机构的输出端与输出构件连接；所述汇流机构的输出端与输出构件连接；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。本发明能够多模式无级变速，并具有能量再利用和应急保障的功能。

Description

一种具有自动调节功能的功率分流式机液复合传动系统 技术领域
本发明涉及车辆变速箱领域，特别涉及一种具有自动调节功能的功率分流式机液复合传动系统。
背景技术
液压机械复合传动采用液压传动实现起步工况，机液传动实现作业工况，机械传动实现转场工况，适应不同的工作情况。就其机液传动而言，主要分为功率分流和功率汇流两种类型。功率分流方式采用2K-H行星齿轮机构前置，主要适用于小功率传动系统；功率汇流方式采用2K-H行星齿轮机构后置，主要适用于大功率传动系统。
传统的液压调速主要采用容积调速方式，通过控制变量泵排量进行调速，作为动力源的发动机较难满足其动力性和燃油经济性的要求，若采用电动机调速，对于以功率汇流方式为代表的大功率传动系统的牵引动力要求则较难满足，但对于以功率分流方式为代表的小功率传动系统的性能提高却是可行方案之一。
车辆传动系统的安全可靠性能和节能减排特性是目前研究的热点，但在机液复合传动中应用不多，集安全可靠和能量利用为一体的液压传动机构能够大大提高机液复合传动系统的性能。
发明内容
针对现有技术中存在的不足，本发明提供了一种具有自动调节功能的功率分流式机液复合传动系统，能够多模式无级变速，并具有能量再利用和应急保障的功能。
本发明是通过以下技术手段实现上述技术目的的。
一种具有自动调节功能的功率分流式机液复合传动系统，包括输入构件、液压传动机构、分流机构、汇流机构、输出构件、离合器组件和制动器组件；所述离合器组件将输入构件与分流机构的输入端连接，将分流机构的输出端分别连接到液压传动机构的输入端和汇流机构的输入端，将液压传动机构的输出端与输出构件连接；所述汇流机构的输出端与输出构件连接；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，提供输入机构与输出构件之间的传动方式包括：液压传动、机液传动和机械传动。
进一步，所述分流机构包括分流机构齿圈、分流机构行星架和分流机构太阳轮；所述分流机构齿圈与输入构件连接；
所述汇流机构包括汇流机构公共齿圈、汇流机构小太阳轮、汇流机构大太阳轮、汇流机构短行星架和汇流机构长行星架；所述汇流机构短行星架与汇流机构长行星架连接，所述汇流机构长行星架与输出构件连接；所述汇流机构公共齿圈、汇流机构小太阳轮和汇流机构短行星架构成一个行星轮系，所述汇流机构公共齿圈、汇流机构大太阳轮和汇流机构长行星架构成另一个行星轮系；
所述离合器组件包括离合器C 1和离合器C 2，所述离合器C 1用于选择性的将分流机构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 2用于选择性的将液压传动机构的输出端与输出构件连接以共同旋转；所述制动器组件包括制动器B 1，所述制动器B 1用于选择性的将分流机构行星架连接到固定件；
接合所述离合器C 1、离合器C 2和制动器B 1，提供输入构件与输出构件之间前进或后退的液压传动。
进一步，所述离合器组件还包括离合器C 3、离合器C 4和离合器C 5；所述离合器C 3用于选择性的将分流机构行星架与汇流机构大太阳轮连接以共同旋转；所述离合器C 4用于选择性的将汇流机构小太阳轮与汇流机构大太阳轮连接以共同旋转；所述离合器C 5用于选择性的将分流机构齿圈与分流机构行星架连接以共同旋转；所述制动器组件还包括制动器B 2和制动器B 3，所述制动器B 2用于选择性的将汇流机构小太阳轮连接到固定件；所述制动器B 3用于选择性的将汇流机构公共齿圈连接到固定件；
接合所述离合器C 3、离合器C 5和制动器B 3，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 3、离合器C 5和制动器B 2，或接合所述离合器C 3、离合器C 4和离合器C 5，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，接合所述离合器C 1、离合器C 2、离合器C 3和制动器B 3，提供输入构件与输出构件之间后退方向的机液传动；
接合所述离合器C 1、离合器C 2、离合器C 3和制动器B 2，或接合所述离合器C 1、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液传动。
进一步，所述液压传动机构包括变量泵、补油系统、电磁换向阀V 3、比例节流阀V 8、安全阀组、三位四通比例方向阀V 9、高压蓄能器A 1、低压蓄能器A 2、应急阀V 10和泵/马达机构，所述变量泵的输入端通过离合器C 1与分流机构的输出连接，所述泵/马达机构的输出端通过离合器C 2与输出构件连接，所述变量泵用于驱动泵/马达机构，所述变量泵的出口与泵/马达机构的进口之间的高压液压管道设有电磁换向阀V 3，用于油液的单向流动；所述变量泵的进口与泵/马达机构的出口之间的低压液压管道设有比例节流阀V 8；所述低压液压管道与高 压液压管道之间并联比例方向阀V 9；所述高压蓄能器A 1和低压蓄能器A 2分别与所述比例方向阀V 9连接；
所述低压液压管道与高压液压管道上分别设有安全阀组，用于调节管路压力；所述补油系统用于补充低压液压管道和/或高压液压管道内的液压油。
进一步，当输出构件减速时，接合所述离合器C 2，使得输出构件的制动能量传递到泵/马达机构；所述泵/马达机构处于液压泵工况下；控制所述电磁换向阀V 3通电，使油液不会倒流至变量泵；控制所述比例节流阀V 8阀口减小，用于以增大泵/马达机构出油口压力；控制所述比例方向阀V 9使所述低压蓄能器A 2与泵/马达机构的进油口连通，用于补充油液；控制所述比例方向阀V 9使所述高压蓄能器A 1与泵/马达机构的出油口连通，用于存储能量。
进一步，当输出构件加速时，所述泵/马达机构处于液压泵工况下；控制所述电磁换向阀V 3通电，使油液不会倒流至变量泵；控制所述比例方向阀V 9使所述低压蓄能器A 2与泵/马达机构的出油口连通；控制所述比例方向阀V 9使所述高压蓄能器A 1与泵/马达机构的进油口连通；所述高压蓄能器A 1单独或高压蓄能器A 1与变量泵共同驱动泵/马达机构；所述低压蓄能器A 2用于回收剩余能量。
进一步，所述低压液压管道与高压液压管道之间还并联应急阀V 10；控制所述应急阀V 10用于切断变量泵对外传递的动力，或切换泵/马达机构对内存储的动力，或释放高压蓄能器A 1和低压蓄能器A 2存储的动力。
本发明的有益效果在于：
1.本发明所述的具有自动调节功能的功率分流式机液复合传动系统，采用液压传动、机液传动和机械传动，适应不同的作业情况。
2.本发明所述的具有自动调节功能的功率分流式机液复合传动系统，通过控制变量泵排量以调节液压传动机构排量比，控制变频器以控制电动机转速，切换相对应离合器组件和制动器组件，提高前进和后退档位的各种传动方式。
3.本发明所述的具有自动调节功能的功率分流式机液复合传动系统，将各类阀、变频器和电动机组成的主动力源、蓄能器组成的辅助动力源和变量泵相结合，提供一种高可靠性和多自由度传动系统。
附图说明
图1为本发明所述的具有自动调节功能的功率分流式机液复合传动系统原理图。
图2为本发明的F(H)/R(H)档位功率流向示意图。
图3为本发明的R(M)档位功率流向示意图。
图4为本发明的F 1(M)档位功率流向示意图。
图5为本发明的F 2(M)档位功率流向示意图。
图6为本发明的R(HM)档位功率流向示意图。
图7为本发明的F 1(HM)档位功率流向示意图。
图8为本发明的F 2(HM)档位功率流向示意图。
图9为本发明的辅助动力源能量回收示意图。
图10为本发明的辅助动力源与电动机共同驱动传动装置示意图。
图11为本发明的泵/马达机构功率释放流向示意图。
图12为本发明的变量泵功率释放流向示意图。
图13为本发明的辅助动力源功率释放流向示意图。
图中：
1-变频器；2-电动机；3-输入轴；4-液压传动机构；41-液压传动输入齿轮副；42-离合器C 1；43-变量泵轴；44-变量泵；45-补油泵；46-电磁换向阀V 3；47-比例节流阀V 8；48-先导比例溢流阀V 7；49-先导比例溢流阀V 6；410-比例方向阀V 9；411-高压蓄能器A 1；412-低压蓄能器A 1；413-应急阀V 10；414-泵/马达机构；415-泵马达机构轴；416-液压传动输出齿轮副；417-离合器C 2；5-分流机构；51-离合器C 5；52-分流机构齿圈；53-分流机构行星架；54-分流机构太阳轮；6-机械传动机构；61-制动器B 1；62-机械传动轴；63-离合器C 3；7-汇流机构；71-制动器B 2；72-离合器C 4；73-制动器B 3；74-汇流机构公共齿圈；75-汇流机构小太阳轮；76-汇流机构大太阳轮；77-汇流机构短行星架；78-汇流机构长行星架；8-输出轴。
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，本发明所述的具有自动调节功能的功率分流式机液复合传动系统，包括变频器1、电动机2、输入轴3、液压传动机构4、分流机构5、机械传动机构6、汇流机构7和输出轴8；所述变频器1通过电动机2带动输入轴3转动。
所述分流机构5包括离合器C 5 51、分流机构齿圈52、分流机构行星架53和分流机构太阳轮54；所述离合器C 5 51用于连接分流机构齿圈52和分流机构行星架53，所述分流机构齿圈52与输入轴3固连，所述分流机构太阳轮54与液压传动机构4的输入端连接，所述分流机构行星架53与机械传动机构6连接；
所述机械传动机构6包括制动器B 1 61、机械传动轴62和离合器C 3 63；所述机械传动轴62用于连接分流机构5和汇流机构7，制动器B 1 61用于制动机械传动轴62，离合器C 3 63用于连接机械传动轴62；
所述汇流机构7包括制动器B 2 71、离合器C 4 72、制动器B 3 73、汇流机构公共齿圈74、 汇流机构小太阳轮75、汇流机构大太阳轮76、汇流机构短行星架77和汇流机构长行星架78；所述汇流机构大太阳轮76与机械传动轴62连接，汇流机构短行星架77和汇流机构长行星架78与输出轴8固连，所述离合器C 472用于连接汇流机构小太阳轮75与机械传动轴62，制动器B 2 71用于制动汇流机构小太阳轮75，制动器B 3 73用于制动汇流机构公共齿圈74。
所述液压传动机构4包括液压传动输入齿轮副41、离合器C 1 42、变量泵轴43、变量泵44、补油泵45、电磁换向阀V 3 46、比例节流阀V 8 47、先导比例溢流阀V 7 48、先导比例溢流阀V 6 49、比例方向阀V 9 410、高压蓄能器A 1 411、低压蓄能器A 2 412、应急阀V 10 413、泵/马达机构414、泵马达机构轴415、液压传动输出齿轮副416和离合器C 2 417；所述泵/马达机构414为可以在液压泵和液压马达之间进行功能切换的装置，即当泵/马达机构414输入机械能，所述泵/马达机构414输出液压能，当泵/马达机构414输入液压能，所述泵/马达机构414输出机械能。所述离合器C 1 42通过液压传动输入齿轮副41连接分流机构5和变量泵轴43，离合器C 2 417通过液压传动输出齿轮副416连接汇流机构7和泵/马达机构轴415；所述变量泵44驱动泵/马达机构414；所述变量泵44和泵/马达机构414的高压液压管道之间设有电磁换向阀V 3 46，用于油液的单向流动；所述变量泵44和泵/马达机构414的低压液压管道之间设有比例节流阀V 8 47；所述变量泵44和泵/马达机构414的高、低压液压管道之间设有相互并联的三位四通比例方向阀V 9 410和应急阀V 10 413，三位四通比例方向阀V 9 410左侧上、下两阀口分别连接高、低压管路，右侧上、下两阀口分别连接高压蓄能器A 1 411、低压蓄能器A 2 412；
所述低压液压管道与高压液压管道上分别设有安全阀组，用于调节管路压力；安全阀组包括两个单向阀、先导比例溢流阀V 7 48和先导比例溢流阀V 6 49，两个单向阀背向串联后并联在低压液压管道与高压液压管道之间；所述先导比例溢流阀V 7 48和先导比例溢流阀V 6 49串联后并联在低压液压管道与高压液压管道之间；所述两个单向阀之间与先导比例溢流阀V 7 48和先导比例溢流阀V 6 49之间设有连通支路。所述补油系统用于补充低压液压管道和/或高压液压管道内的液压油。补油系统包括补油泵45、溢流阀V 1和单向阀V 2。补油系统出口端与所述支路连通。
如表1所示，通过调节液压传动机构4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，提供输入机构与输出构件之间的传动方式包括：液压传动、机液传动和机械传动。
液压传动包括R(H)档和F(H)档，具体如下：
F(H)/R(H)档位功率流向如图2所示。当接合离合器C 1 42、离合器C 2 417和制动器B 1 61时，变频器1驱动电动机2输出的动力，经输入轴3、分流机构齿圈52、分流机构太阳 轮54和液压传动机构4，从输出轴8输出。此时，输出转速与输入转速关系为：
n o＝en E
式中，n E为电动机转速，n o为输出转速，e为液压传动机构的排量比。
当电动机转向为正时，输出转速为正；电动机转速为负时，输出转速为负。
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3所示。当接合离合器C 3 63、离合器C 5 51和制动器B 3 73时，变频器1驱动电动机2输出的动力，经输入轴3、固连为一体的分流机构5、机械传动机构6、汇流机构大太阳轮76和汇流机构长行星架78，从输出轴8输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106688-appb-000001
F 1(M)档位功率流向如图4所示。当接合离合器C 3 63、离合器C 5 51和制动器B 2 71时，变频器1驱动电动机2输出的动力，经输入轴3、固连为一体的分流机构5、机械传动机构6、汇流机构大太阳轮76、汇流机构公共齿圈74、和汇流机构长行星架78，从输出轴8输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106688-appb-000002
F 2(M)档位功率流向如图5所示。当接合离合器C 3 63、离合器C 4 72和离合器C 5 51时，变频器1驱动电动机2输出的动力，经输入轴3、固连为一体的分流机构5、机械传动机构6、固连为一体的汇流机构7，从输出轴8输出。此时，输出转速与输入转速关系为：
n o＝n E。
机械传动包括R(HM)档、F 1(HM)档和F 2(HM)档，具体如下：
R(HM)档位功率流向如图6所示。当接合离合器C 1 42、离合器C 2 417、离合器C 3 63和制动器B 3 73时，变频器1驱动电动机2输出的动力，经输入轴3、分流机构齿圈52分为两路，一路经分流机构行星架53、机械传动轴62和汇流机构大太阳轮76，传递到汇流机构长行星架78，一路经分流机构太阳轮54、液压传动机构4，传递到汇流机构长行星架78，混合动力经汇流机构长行星架78汇合，从输出轴8输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106688-appb-000003
F 1(HM)档位功率流向如图7所示。当接合离合器C 1 42、离合器C 2 417、离合器C 3 63 和制动器B 2 71时，变频器1驱动电动机2输出的动力，经输入轴3、分流机构齿圈52分为两路，一路经分流机构行星架53、机械传动轴62、汇流机构大太阳轮76和汇流机构公共齿圈74，传递到汇流机构长行星架78，一路经分流机构太阳轮54、液压传动机构4，传递到汇流机构长行星架78，混合动力经汇流机构长行星架78汇合，从输出轴8输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106688-appb-000004
F 2(HM)档位功率流向如图8所示。当接合离合器C 1 42、离合器C 2 417、离合器C 3 63和离合器C 4 72时，变频器1驱动电动机2输出的动力，经输入轴3、分流机构齿圈52分为两路，一路经分流机构行星架53和机械传动轴62、传递到固连为一体的汇流机构7，一路经分流机构太阳轮54、液压传动机构4，传递到固连为一体的汇流机构7，混合动力从输出轴8输出。此时，输出转速与输入转速关系为：
Figure PCTCN2020106688-appb-000005
表1各元件接合表
Figure PCTCN2020106688-appb-000006
其中：“▲”代表元件处于接合状态；
主要参数：n o为输出轴转速，n E为电动机转速，e为液压传动机构的排量比，i为相关齿轮的传动比，i m为不同档位汇流机构的传动比；i 1i 2＝1.00，k＝1.5，i m1＝-1.82，i m2＝1.82，i m3＝1.00。
“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。
各种传动方式，在液压传动机构的排量比不变的前提下，皆可通过调节电动机转速进行无级调速，且输出轴转速方向由电动机转速方向确定。也可通过调节变量泵排量进而控制液压传动机构的排量比，以及控制变频器进而调节电动机的转速共同调节。
液压传动机构的排量比范围为：e∈[0,1]。当电动机转向为正时，F(H)档位调速范围为n 0∈[0,n Emax]；当电动机转向为负时，R(H)档位调速范围为n 0∈[-n Emax,0]。
以下以电动机转向为正进行说明，电动机转向为负同理可得。
R(M)档位调速范围为：n 0∈[-0.55n Emax,0]；
F 1(M)档位调速范围为：n 0∈[0,0.55n Emax]；
F 2(M)档位调速范围为：n 0∈[0,n Emax]；
R(HM)档位调速范围为：n 0∈[-0.27n Emax,0]；
F 1(HM)档位和F 2(HM)档位需经F(H)档位切换可得，且两档位液压传动机构的排量比取值范围为：e∈[0.50,1.00]；
即当电动机转速相同时，当e＝0.55时，F(H)档位可与F 1(HM)档位同步换挡。F 1(HM)档位取值范围为：n 0∈[0,0.59n Emax]。
即当电动机转速相同时，当e＝1.00时，F(H)档位可与F 2(HM)档位同步换挡。F 2(HM)档位取值范围为：n 0∈[0,3n Emax]。
系统负向传动可有两种实现方式：
①R(H)档位，通过电动机反向旋转和调节液压传动机构的排量比来实现，调速范围为n 0∈[-n Emax,0]；
②R(M)档位，通过电动机正向旋转来实现，调速范围为n 0∈[-0.55n Emax,0]；
③R(HM)档位，通过电动机正向旋转和调节液压传动机构的排量比来实现，调速范围为n 0∈[-0.27n Emax,0]。
当电动机正向旋转时，系统正向传动可有五种实现方式：
④F(H)档位，通过电动机正向旋转和调节液压传动机构的排量比来实现，调速范围为n 0∈[0,n Emax]；
⑤F 1(M)档位，通过电动机正向旋转来实现，调速范围为n 0∈[0,0.55n Emax]；
⑥F 2(M)档位，通过电动机正向旋转来实现，调速范围为n 0∈[0,n Emax]；
⑦F(H)档位切换到F 1(HM)档位，当电动机转速相同时，同步换挡点为e＝0.55，当e∈[0.50,1.00]时，通过电动机正向旋转和调节液压传动机构的排量比来实现，调速范围为n 0∈[0,0.59n Emax]；
⑧F(H)档位切换到F 2(HM)档位，当电动机转速相同时，同步换挡点为e＝1.00，当e∈[0.50,1.00]时，通过电动机正向旋转和调节液压传动机构的排量比来实现，调速范围为n 0∈[0,3n Emax]。
如图9所示，车辆减速时，离合器C 2 417接合，使得制动能量经输出轴8和液压传动输出齿轮副416，传递到泵/马达机构414。此时泵/马达机构414处于液压泵工况下，电磁换向阀V 3 46通电保证外部油液不会倒流至变量泵44，比例节流阀V 8 47阀口减小以增大泵/马达机构414出油口压力，三位四通比例方向阀V 9410处于下位，先导比例溢流阀V 7 48调定系统安全压力，并保证充油过程的实现。当泵/马达机构414出油口压力大于高压蓄能器A 1 411设定压力时，泵/马达机构414的出油口向高压蓄能器A 1 411存储能量，低压蓄能器A 2 412可向泵/马达机构414的进油口补充油液。
如图10所示，车辆加速时，此时泵/马达机构414处于液压马达工况下，电磁换向阀V 3 46通电保证外部油液不会倒流至变量泵44，三位四通比例方向阀V 9 410处于上位，先导比例溢流阀V 6 49调定系统安全压力，并保证放油过程的实现。高压蓄能器A 1 411单独，或和变量泵44共同释放能量驱动泵/马达机构414运行，低压蓄能器A 2 412可回收剩余能量。
如图11所示，泵/马达机构414处于液压泵工况下，电磁换向阀V 3 46通电保证外部油液不会倒流至变量泵44，应急阀V 10 413通电，泵/马达机构414进、出油口压力相等，制动能量无法进一步存储到蓄能机构或传递到变量泵44。
如图12所示，泵/马达机构414处于液压马达工况下，电磁换向阀V 3 46通电保证外部油液不会倒流至变量泵44，应急阀V 10 413通电，变量泵44进、出油口压力相等，能量无法进一步传递到泵/马达机构414。
如图13所示，电磁换向阀V 346通电保证外部油液不会倒流至变量泵44，应急阀V 10 413通电，高压蓄能器A 1 411和低压蓄能器A 2 412相通，最后两蓄能器压力相同。
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 (9)

  1. 一种具有自动调节功能的功率分流式机液复合传动系统，其特征在于，包括输入构件、液压传动机构(4)、分流机构(5)、汇流机构(7)、输出构件、离合器组件和制动器组件；所述离合器组件将输入构件与分流机构(5)的输入端连接，将分流机构(5)的输出端分别连接到液压传动机构(4)的输入端和汇流机构(7)的输入端，将液压传动机构(4)的输出端与输出构件连接；所述汇流机构(7)的输出端与输出构件连接；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所述的具有自动调节功能的功率分流式机液复合传动系统，其特征在于，通过调节液压传动机构(4)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，提供输入机构与输出构件之间的传动方式包括：液压传动、机液传动和机械传动。
  3. 根据权利要求2所述的具有自动调节功能的功率分流式机液复合传动系统，其特征在于，所述分流机构(5)包括分流机构齿圈(52)、分流机构行星架(53)和分流机构太阳轮(54)；所述分流机构齿圈(52)与输入构件连接；
    所述汇流机构(7)包括汇流机构公共齿圈(74)、汇流机构小太阳轮(75)、汇流机构大太阳轮(76)、汇流机构短行星架(77)和汇流机构长行星架(78)；所述汇流机构短行星架(77)与汇流机构长行星架(78)连接，所述汇流机构长行星架(78)与输出构件连接；所述汇流机构公共齿圈(74)、汇流机构小太阳轮(75)和汇流机构短行星架(77)构成一个行星轮系，所述汇流机构公共齿圈(74)、汇流机构大太阳轮(76)和汇流机构长行星架(78)构成另一个行星轮系；
    所述离合器组件包括离合器C 1(42)和离合器C 2(417)，所述离合器C 1(42)用于选择性的将分流机构太阳轮(54)与液压传动机构(4)的输入端连接以共同旋转；所述离合器C 2(417)用于选择性的将液压传动机构(4)的输出端与输出构件连接以共同旋转；所述制动器组件包括制动器B 1(61)，所述制动器B 1(61)用于选择性的将分流机构行星架(53)连接到固定件；
    接合所述离合器C 1(42)、离合器C 2(417)和制动器B 1(61)，提供输入构件与输出构件之间前进或后退的液压传动。
  4. 根据权利要求3所述的具有自动调节功能的功率分流式机液复合传动系统，其特征在于，所述离合器组件还包括离合器C 3(63)、离合器C 4(72)和离合器C 5(51)；所述离合器C 3(63)用于选择性的将分流机构行星架(53)与汇流机构大太阳轮(76)连接以共同旋转；所述离合器C 4(72)用于选择性的将汇流机构小太阳轮(75)与汇流机构大太阳轮(76)连接以共同旋转；所述离合器C 5(51)用于选择性的将分流机构齿圈(52)与分流机构行星架(53)连接以共同旋转；所述制动器组件还包括制动器B 2(71)和制动器B 3(73)，所述 制动器B 2(71)用于选择性的将汇流机构小太阳轮(75)连接到固定件；所述制动器B 3(73)用于选择性的将汇流机构公共齿圈(74)连接到固定件；
    接合所述离合器C 3(63)、离合器C 5(51)和制动器B 3(73)，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 3(63)、离合器C 5(51)和制动器B 2(71)，或接合所述离合器C 3(63)、离合器C 4(72)和离合器C 5(51)，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。
  5. 根据权利要求4所述的具有自动调节功能的功率分流式机液复合传动系统，其特征在于，接合所述离合器C 1(42)、离合器C 2(417)、离合器C 3(63)和制动器B 3(73)，提供输入构件与输出构件之间后退方向的机液传动；
    接合所述离合器C 1(42)、离合器C 2(417)、离合器C 3(63)和制动器B 2(71)，或接合所述离合器C 1(42)、离合器C 2(417)、离合器C 3(63)和离合器C 4(72)，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液传动。
  6. 根据权利要求1所述的具有自动调节功能的功率分流式机液复合传动系统，其特征在于，所述液压传动机构(4)包括变量泵(44)、补油系统、电磁换向阀V 3(46)、比例节流阀V 8(47)、安全阀组、三位四通比例方向阀V 9(410)、高压蓄能器A 1(411)、低压蓄能器A 2(412)、应急阀V 10(413)和泵/马达机构(414)，所述变量泵(44)的输入端通过离合器C 1(42)与分流机构(5)的输出连接，所述泵/马达机构(414)的输出端通过离合器C 2(417)与输出构件连接，所述变量泵(44)用于驱动泵/马达机构(414)，所述变量泵(44)的出口与泵/马达机构(414)的进口之间的高压液压管道设有电磁换向阀V 3(46)，用于油液的单向流动；所述变量泵(44)的进口与泵/马达机构(414)的出口之间的低压液压管道设有比例节流阀V 8(47)；所述低压液压管道与高压液压管道之间并联比例方向阀V 9(410)；所述高压蓄能器A 1(411)和低压蓄能器A 2(412)分别与所述比例方向阀V 9(410)连接；
    所述低压液压管道与高压液压管道上分别设有安全阀组，用于调节管路压力；所述补油系统用于补充低压液压管道和/或高压液压管道内的液压油。
  7. 根据权利要求6所述的具有自动调节功能的功率分流式机液复合传动系统，其特征在于，当输出构件减速时，接合所述离合器C 2(417)，使得输出构件的制动能量传递到泵/马达机构(414)；所述泵/马达机构(414)处于液压泵工况下；控制所述电磁换向阀V 3(46)通电，使油液不会倒流至变量泵(44)；控制所述比例节流阀V 8(47)阀口减小，用于以增大泵/马达机构(414)出油口压力；控制所述比例方向阀V 9(410)使所述低压蓄能器A 2(412)与泵/马达机构(414)的进油口连通，用于补充油液；控制所述比例方向阀V 9(410)使所述高压蓄能器A 1(411)与泵/马达机构(414)的出油口连通，用于存储能量。
  8. 根据权利要求6所述的具有自动调节功能的功率分流式机液复合传动系统，其特征在于，当输出构件加速时，所述泵/马达机构(414)处于液压泵工况下；控制所述电磁换向阀V 3(46)通电，使油液不会倒流至变量泵(44)；控制所述比例方向阀V 9(410)使所述低压蓄能器A 2(412)与泵/马达机构(414)的出油口连通；控制所述比例方向阀V 9(410)使所述高压蓄能器A 1(411)与泵/马达机构(414)的进油口连通；所述高压蓄能器A 1(411)单独或高压蓄能器A 1(411)与变量泵(44)共同驱动泵/马达机构(414)；所述低压蓄能器A 2(412)用于回收剩余能量。
  9. 根据权利要求6所述的具有自动调节功能的功率分流式机液复合传动系统，其特征在于，所述低压液压管道与高压液压管道之间还并联应急阀V 10(413)；控制所述应急阀V 10(413)用于切断变量泵(44)对外传递的动力，或切换泵/马达机构(414)对内存储的动力，或释放高压蓄能器A 1(411)和低压蓄能器A 2(412)存储的动力。
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