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WO2019195992A1 - 一种工程机械用三段式机械复合无级传动装置 - Google Patents

一种工程机械用三段式机械复合无级传动装置 Download PDF

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Publication number
WO2019195992A1
WO2019195992A1 PCT/CN2018/082412 CN2018082412W WO2019195992A1 WO 2019195992 A1 WO2019195992 A1 WO 2019195992A1 CN 2018082412 W CN2018082412 W CN 2018082412W WO 2019195992 A1 WO2019195992 A1 WO 2019195992A1
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WIPO (PCT)
Prior art keywords
gear
twenty
shaft
clutch
hydraulic
Prior art date
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PCT/CN2018/082412
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English (en)
French (fr)
Inventor
彭增雄
胡纪滨
荆崇波
吴维
周俊杰
魏超
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Beijing Institute of Technology BIT
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Beijing Institute of Technology BIT
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Priority to EP18914723.4A priority Critical patent/EP3779238B1/en
Priority to PCT/CN2018/082412 priority patent/WO2019195992A1/zh
Publication of WO2019195992A1 publication Critical patent/WO2019195992A1/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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/40—Special vehicles
    • B60Y2200/41—Construction vehicles, e.g. graders, excavators
    • B60Y2200/415—Wheel loaders
    • 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
    • F16H37/084—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 at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power-split transmissions with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • F16H2037/0886—Power-split transmissions with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges

Definitions

  • the invention belongs to the technical field of power transmission, and relates to a stepless transmission device, and more specifically to a three-stage mechanical composite stepless transmission device for engineering machinery.
  • the mechanical mechanical loader generally adopts the hydraulic mechanical power shifting gearbox. Due to the need of the loading operation, the vehicle speed and the engine load change drastically, the torque converter efficiency is low, resulting in the highest transmission efficiency of the transmission system is about 75%.
  • Hydrostatic transmission can easily realize stepless speed regulation, so that the loader engine often works in the economic speed range, which can improve the energy utilization efficiency of the whole vehicle; however, the efficiency of the hydraulic pump/motor closed speed control loop used for hydrostatic transmission is also Lower, so the potential for hydrostatic transmission is limited compared to the power-shift hydraulic mechanical gearbox.
  • the hydraulic mechanical transmission can realize high-efficiency stepless transmission through the combination of mechanical power and hydraulic power, so that the engine maintains a stable load, which is beneficial to improve fuel economy and become one of the development directions of the loader transmission system. Actively carry out research on this transmission technology.
  • Dana Rexroth's patent US 2014/0305113 A1 discloses a two-stage hydraulic mechanical transmission that starts with pure hydraulic section and hydraulic mechanical section operation and walking.
  • Dana Rexroth's patent EP 2280192 B1 discloses a three-stage hydraulic mechanical transmission that starts with a pure hydraulic section and two hydraulic mechanical sections for operation and travel, respectively, for higher transmission efficiency. However, both schemes start with a hydraulic section and the efficiency is lower than that of the hydraulic mechanical section.
  • ZF company US8328676 B2 discloses a hydraulic mechanical transmission for loaders, using two or three hydraulic mechanical sections, using split split and split split power splitting, transmission efficiency higher.
  • the hydraulic components required to adopt these two power split forms have higher power and higher cost.
  • the object of the present invention is to provide a three-stage continuous hydraulic mechanical transmission device for construction machinery, which eliminates a pure hydraulic section with low efficiency, and realizes three hydraulic mechanical sections for low speed operation, medium speed walking and High-speed walking; the speed of the hydraulic components in the three working sections continuously changes, the power of the required hydraulic components is small, the operation is simple, and the transmission efficiency is high.
  • the reverse gear contains two hydraulic mechanical sections to meet the reverse speed requirements.
  • a three-stage mechanical composite stepless transmission device for engineering machinery comprising a casing, a main input shaft, a main output shaft, a hydraulic pump and a hydraulic motor;
  • One end of the main input shaft is electrically connected to an engine block of the construction machine, and the other end of the main input shaft is dynamically connected to a working pump, the main input shaft runs through the casing and is movably connected with the casing, the main a fifth gear is fixedly disposed on the input shaft;
  • the main output shaft is used for the driving, the work and the steering output power of the construction machine, the main output shaft is movably connected to the housing, and the second output gear is fixedly disposed on the main output shaft;
  • a power input shaft of the hydraulic pump is movably connected to the housing, a portion of the hydraulic pump whose power input shaft is located in the housing is fixedly disposed with a fourth gear, and the fourth gear is coupled to the fifth gear Engage
  • the power output shaft of the hydraulic motor is movably connected to the housing, and a portion of the power output shaft of the hydraulic motor located in the housing is fixedly disposed with a second twelve gear;
  • the hydraulic pump and the hydraulic motor form a closed hydraulic circuit
  • the first half shaft is movably connected to the housing, the other end is fixedly provided with an eighth sun gear, and the first half shaft is provided with a sixth gear, the sixth gear Engaging with the fifth gear;
  • the second half shaft is further disposed coaxially with the first half shaft, one end of the second half shaft is movably connected to the casing, and the other end is fixedly provided with a tenth sun wheel; a first K2 clutch and a first K3 clutch are disposed on the second half shaft, and the seventeenth gear and the fifteenth gear are disposed on the second half shaft, the seventeenth gear and the first An active end power connection of the K3 clutch, the fifteenth gear being in power connection with the active end of the first K2 clutch;
  • An eleventh planet carrier is further disposed on the eleventh planet carrier with a plurality of seventh planet gears and a plurality of ninth planet gears, the seventh planet gear being dynamically coupled to the eighth sun gear, a ninth planetary wheel is dynamically coupled to the tenth sun gear;
  • the eleventh planet carrier is fixedly coupled to a first K1 clutch, and the active end of the first K1 clutch is dynamically connected to the fifteenth gear;
  • the first intermediate shaft is disposed in the housing and is movably connected to the housing, and the first intermediate shaft is provided with a nineteenth gear and a second eleven gear.
  • the nineteenth gear meshes with the twenty-second gear
  • the twenty-first gear is meshed with the fifteenth gear
  • the first intermediate shaft is fixedly disposed with a second fourteen a gear and a twenty-fifth gear
  • the twenty-fourth gear meshes with the seventeenth gear
  • the twenty-fifth gear meshes with the twenty-ninth gear
  • the first intermediate shaft a first KV clutch is further disposed, and an active end of the first KV clutch is engaged with the second eleven gear;
  • a second intermediate shaft a twenty-eighth gear and a twenty-sixth gear, wherein the twenty-eighth gear is fixedly disposed on the second intermediate shaft, and the second sixteen gear is rotatably disposed on the On the two intermediate shafts, the twenty-eighth gear is meshed with the twenty-ninth gear, and the second intermediate shaft is further provided with a first KR clutch, the active end of the first KR clutch and the The twenty-sixth gear meshes;
  • a twelfth gear and a thirteenth gear that are coaxially fixedly disposed, the twelfth gear meshing with the ninth gear, and the thirteenth gear meshes with the nineteenth gear.
  • a charge pump is further included, and the charge pump is dynamically connected to the hydraulic pump.
  • the hydraulic and mechanical power is combined.
  • the hydraulic circuit only transmits part of the power. Most of the power is transmitted through the mechanical path to achieve high transmission efficiency and stepless speed change, which can improve work efficiency and reduce engine fuel consumption.
  • stepless speed regulation can make the engine work at economic speed, improve fuel economy and reduce engine noise.
  • the power shift can be realized. Firstly, the clutch of the next section is engaged, and then the clutch of the previous section is released to ensure the uninterrupted output of the power, thereby improving the work efficiency.
  • the other parts adopt fixed-axis gear transmission, which can realize the center drop of the input and output of the loader transmission on the one hand, and reduce the process and processing cost on the other hand.
  • Figure 1 is a schematic diagram of the transmission of the hydraulic mechanical composite stepless transmission device of the present invention
  • Figure 2 is a diagram showing the rotational speed of the hydraulic pump and the motor of the present invention
  • Figure 3 is a maximum pressure diagram of the hydraulic pump of the present invention.
  • Figure 4 is a diagram showing the maximum output torque of the present invention.
  • Figure 5 is an efficiency diagram of the present invention.
  • the three-stage mechanical composite stepless transmission device for construction machinery of the present invention comprises a casing 1, a main input shaft 30, a main output shaft 31, a hydraulic pump 2 and a hydraulic motor 20; One end of 30 is electrically connected to the engine block of the construction machine, and the other end of the main input shaft 30 is dynamically connected to a working pump 32.
  • the main input shaft 30 extends through the casing 1 and is movably connected to the casing 1.
  • a fifth gear 5 is fixedly disposed on the main input shaft 30; the main output shaft 31 is for outputting power for walking, work and steering of a construction machine, and the main output shaft 31 is movably connected to the casing 1, A second nineteen gear 29 is fixedly disposed on the main output shaft 31; a power input shaft of the hydraulic pump 2 is movably connected to the housing 1, and a power input shaft of the hydraulic pump 2 is located in the housing 1 Partly fixedly provided with a fourth gear 4, the fourth gear 4 meshes with the fifth gear 5; a power output shaft of the hydraulic motor 20 is movably connected to the housing 1, and the power of the hydraulic motor 20 a portion of the output shaft located in the housing 1 is fixedly provided with a first portion a twelve-wheel gear 22; the hydraulic pump 2 and the hydraulic motor 20 form a closed hydraulic circuit; further comprising a first half shaft, one end of the first half shaft is movably connected to the casing 1, and the other end is fixedly disposed An eighth sun gear 8 is provided with a sixth gear 6 on the
  • the three-stage mechanical composite stepless transmission device for construction machinery of the present invention has the shifting logic as shown in the following table (indicating the clutch to be engaged):
  • the first section is a hydraulic mechanical section I
  • the engine input power is input through the main input shaft 30, and on the other hand, is transmitted to the hydraulic pump 2 via the fifth gear 5 and the fourth gear 4, and the hydraulic pump 2 and the hydraulic motor 20 form a closed loop, hydraulic
  • the rotation of the pump 2 causes the hydraulic motor 20 to rotate synchronously, while the hydraulic pump 2 drives the charge pump 3 to operate, providing the entire vehicle with the oil pressure required for operation and steering; on the other hand, it is transmitted to the eighth sun gear 8 via the sixth gear 6.
  • the first K1 clutch 14 and the first KV clutch 23 are both engaged, and the power on the eighth sun gear 8 is transmitted to the first K1 clutch 14 via the seventh planetary gear 7 and the ninth planetary gear 9, the first K1 clutch 14 Driving the fifteenth gear 15, the power is transmitted to the twenty-fifth gear 25 through the fifteenth gear 15, the twenty-first gear 21 and the first KV clutch 23, and the twenty-fifth gear 25 is passed through the twenty-ninth gear 29 is passed to the main output shaft 31.
  • the second stage is the hydraulic mechanical section II.
  • the seventh planetary gear 7, the eighth sun gear 8, the ninth planetary gear 9 and the tenth sun gear 10 are formed.
  • the differential structure can first engage the first K2 clutch 16 and then separate the first K1 clutch 14 to ensure uninterrupted power output and improve work efficiency.
  • the engine input power is input through the main input shaft 30, and on the other hand, is transmitted to the hydraulic pump 2 via the fifth gear 5 and the fourth gear 4, the hydraulic pump 2 and the hydraulic motor 20 form a closed circuit, and the hydraulic pump 2 rotates to make the hydraulic motor 20 synchronous rotation, while the hydraulic pump 2 drives the charge pump 3 to work, providing the whole vehicle with the oil pressure required for work and steering; on the other hand, the sixth gear 6 is transmitted to the eighth sun gear 8, the eighth sun gear 8
  • the power is transmitted to the tenth sun gear 10 via the seventh planetary gear 7 and the ninth planetary gear 9, and then transmitted to the first K2 clutch 16, the fifteenth gear 15, the twenty-first gear 21, and the first KV clutch 23 to
  • the twenty-fifth gear 25 is further transmitted from the twenty-fifth gear 25 to the main output shaft 31 via the twenty-ninth gear 29.
  • the third stage is the hydraulic mechanical section III. At this time, only the first K3 clutch 18 is engaged, the engine input power is input through the main input shaft 30, and on the other hand, is transmitted to the hydraulic pump 2 via the fifth gear 5 and the fourth gear 4, and the hydraulic pressure is applied.
  • the pump 2 and the hydraulic motor 20 form a closed circuit, the hydraulic pump 2 rotates to synchronously rotate the hydraulic motor 20, and the hydraulic pump 2 drives the charge pump 3 to work, providing the whole vehicle with the oil pressure required for work and steering;
  • the six gears 6 are transmitted to the eighth sun gear 8, and the power on the eighth sun gear 8 is transmitted to the tenth sun gear 10 via the seventh planetary gear 7 and the ninth planetary gear 9, and then passes through the first K3 clutch 18, the seventeenth The gear 17, the twenty-fourth gear 24, and the twenty-ninth gear 29 are transmitted to the main output shaft 31.
  • the incoming power of the engine is transmitted through a mechanical road and a hydraulic circuit.
  • the mechanical road is the power transmission between the gears and the clutch.
  • the hydraulic circuit is the hydraulic pump 2 and the hydraulic motor 20.
  • the twenty-second gear 22 is transmitted to the ninth gear through the nineteenth gear 19, the thirteenth gear 13 and the twelfth gear 12, and most of the power is transmitted through the mechanical path, and the hydraulic circuit transmits only a small amount of power, thereby realizing High transmission efficiency and stepless speed change achieve the technical effect of improving work efficiency and reducing engine fuel consumption.
  • Figure 2 is the hydraulic pump 2, variable motor speed diagram, in the figure, curve 1 is the pure hydraulic section variable motor speed, curve 2 is the hydraulic mechanical I section variable motor speed, curve 3 is the hydraulic mechanical II section variable motor speed, curve 4 is The speed of the hydraulic pump 2.
  • curve 3 is a maximum pressure diagram of the hydraulic pump 2 of the present invention.
  • curve 1 represents the working pressure of the hydraulic pump 2 of the pure hydraulic section
  • curve 2 represents the working pressure of the hydraulic pump 2 of the hydraulic mechanical section I
  • curve 3 represents the section of the hydraulic machine 2
  • the hydraulic pump 2 works at a pressure.
  • Figure 4 is a graph of the maximum output torque of the present invention.
  • curve 1 represents the maximum output torque of the pure hydraulic section
  • curve 2 represents the maximum output torque of the hydraulic mechanical section I
  • curve 3 represents the maximum output of the hydromechanical section II. Torque.
  • Figure 5 is an efficiency diagram of the present invention.
  • the solid line 1 is the efficiency curve of the hydraulic mechanical section I
  • the solid line 2 is the efficiency curve of the hydraulic mechanical section II
  • the solid line 3 is the efficiency curve of the hydraulic mechanical section III
  • the broken line is The efficiency curve of the loader's traditional four-speed hydraulic mechanical power shift gearbox.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Control Of Transmission Device (AREA)
  • Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)

Abstract

一种工程机械用三段式机械复合无级传动装置，采用三个液压机械段，分别用于低速作业、中速行走和高速行走；三个工作段液压元件的速度连续变化，所需液压元件的功率较小，操纵简单，传动效率高。倒车挡包含两个液压机械段，满足倒车的车速要求。

Description

一种工程机械用三段式机械复合无级传动装置 技术领域
本发明属于动力传动技术领域，涉及一种无级传动装置，更确切的说是一种工程机械用三段式机械复合无级传动装置。
背景技术
目前，工程机械装载机普遍采用液力机械动力换挡变速箱，由于装载作业的需要，车速及发动机负荷变化剧烈，液力变矩器效率较低，导致传动系统最高传动效率约为75％。
静液传动可方便实现无级调速，使装载机发动机常工作于经济转速区间，可提高整车的能源利用效率；但由于静液传动所用的液压泵/马达闭式调速回路的效率也较低，故较动力换挡液力机械变速箱，静液传动的提升潜力有限。
液压机械传动通过机械功率和液压功率的复合，可实现高效的无级传动，使发动机维持稳定的负荷，有利于提高燃油经济性，成为装载机传动系统的发展方向之一，国内外工程机械厂家积极开展该传动技术的研究。
Dana Rexroth公司专利US 2014/0305113 A1公布了一种两段式液压机械传动装置，纯液压段起步以及液压机械段作业及行走。Dana Rexroth公司专利EP2280192B1公布了一种三段式液压机械传动装置，纯液压段起步，两个液压机械段分别用于作业和行走，可获得较高的传动效率。但两种方案均采用液压段起步，效率较液压机械段起步低。
ZF公司US8328676 B2公布了一种装载机液压机械传动装置，采用两个或者三个液压机械段，采用分速汇矩(Output split)和分速汇速(Compound split)的功率分流形式，传动效率更高。但采用这两种功率分流形式所需的液压元件功率较大，成本较高。
发明内容
本发明的目的在于提供本发明提供一种工程机械用三段连续式液压机械传动装置，取消了效率低的纯液压段，采用实现三个液压机械段，分别用于低速作业、中速行走和高速行走；三个工作段液压元件的速度连续 变化，所需液压元件的功率较小，操纵简单，传动效率高。倒车挡包含两个液压机械段，满足倒车的车速要求。
本发明的技术方案如下：
一种工程机械用三段式机械复合无级传动装置，包括壳体、主输入轴、主输出轴、液压泵和液压马达；
所述主输入轴一端与工程机械的发动机组动力连接，所述主输入轴另一端动力连接一作业泵，所述主输入轴贯穿所述壳体并与所述壳体活动连接，所述主输入轴上固定设置有一第五齿轮；
所述主输出轴用于为工程机械的行走、作业和转向输出动力，所述主输出轴与所述壳体活动连接，所述主输出轴上固定设置有一第二十九齿轮；
所述液压泵的动力输入轴与所述壳体活动连接，所述液压泵的动力输入轴位于所述壳体内的部分固定设置有一第四齿轮，所述第四齿轮与所述第五齿轮相啮合；
所述液压马达的动力输出轴与所述壳体活动连接，所述液压马达的动力输出轴位于所述壳体内的部分固定设置有一第二十二齿轮；
所述液压泵与所述液压马达组成闭式液压回路；
还包括第一半轴，所述第一半轴一端与所述壳体活动连接，另一端固定设置有一第八太阳轮，所述第一半轴上设置有一第六齿轮，所述第六齿轮与所述第五齿轮相啮合；
还包括第二半轴，所述第二半轴与所述第一半轴同轴设置，所述第二半轴一端与所述壳体活动连接，另一端固定设置有一第十太阳轮；所述第二半轴上设置有一第一K2离合器以及一第一K3离合器，所述第二半轴上转动设置有第十七齿轮和第十五齿轮，所述第十七齿轮与所述第一K3离合器的主动端动力连接，所述第十五齿轮与所述第一K2离合器的主动端动力连接；
还包括第十一行星架，所述第十一行星架上设置有多个第七行星轮和多个第九行星轮，所述第七行星轮与所述第八太阳轮动力连接，所述第九行星轮与所述第十太阳轮动力连接；
所述第十一行星架固定连接有一第一K1离合器，所述第一K1离合器的主动端与所述第十五齿轮动力连接；
还包括一第一中间轴，所述第一中间轴设置于所述壳体内并与所述壳体活动连接，所述第一中间轴上活动设置有一第十九齿轮以及一第二十一齿轮，所述第十九齿轮与所述第二十二齿轮相啮合，所述第第二十一齿轮与所述第十五齿轮相啮合，所述第一中间轴上固定设置有一第二十四齿轮以及一第二十五齿轮，所述第二十四齿轮与所述第十七齿轮相啮合，所述第二十五齿轮与所述第二十九齿轮相啮合，所述第一中间轴上还设置有一第一KV离合器，所述第一KV离合器的主动端与所述第二十一齿轮相啮合；
还包括第二中间轴、第二十八齿轮和第二十六齿轮，所述第二十八齿轮固定设置于所述第二中间轴上，所述第二十六齿轮转动设置于所述第二中间轴上，所述第二十八齿轮与所述第二十九齿轮相啮合，所述第二中间轴上还设置有一第一KR离合器，所述第一KR离合器的主动端与所述第二十六齿轮相啮合；
还包括同轴固定设置的第十二齿轮和第十三齿轮，所述第十二齿轮与所述第九齿轮相啮合，所述第十三齿轮与所述第十九齿轮相啮合。
可选的，还包括补油泵，所述补油泵与所述液压泵动力连接。
本发明有益效果是：
(1)采用液压与机械的功率复合，液压路只传递部分功率，大部分功率通过机械路传递，实现高传动效率及无级变速，可提高作业效率和降低发动机的油耗。
(2)采用内外啮合双联行星排分汇流机构，可实现三个连续的液压机械段，第Ⅰ段用于低速作业，第Ⅱ段用于中速作业以及行驶工况，第Ⅲ段用于高速行走；液压机械段起步，可提高低速的传动效率；段间切换只需操纵1个离合器，可实现平滑切换。
(3)实现无级调速，可使发动机常工作于经济转速，提高了燃油经济性，降低了发动机的噪声。
(4)可实现段间离合器的零速差切换，提高了离合器摩擦片的寿命，简化了换挡逻辑和操纵系统的设计。
(5)由于液压调速系统的存在，可实现动力换挡，先接合下一段的离合器，再松开上一段的离合器，保证动力的不中断输出，提高了作业效 率。
(6)除分汇流机构，其他部分采用定轴齿轮传动，一方面可实现装载机传动装置输入和输出的中心降距，另一方面可降低工艺和加工成本。
附图说明
图1为本发明的液压机械复合无级传动装置的传动简图；
图2为本发明的液压泵与马达转速图；
图3为本发明的液压泵最大压力图；
图4为本发明的最大输出转矩图；
图5为本发明的效率图。
其中，1-壳体、2-液压泵、3-补油泵、4-第四齿轮、5-第五齿轮、6-第六齿轮、7-第七行星轮、8-第八太阳轮、9-第九行星轮、10-第十太阳轮、11-第十一行星架、12-第十二齿轮、13-第十三齿轮、14-第一K1离合器、15-第十五齿轮、16-第一K2离合器、17-第十七齿轮、18-第一K3离合器、19-第十九齿轮、20-液压马达、21-第二十一齿轮、22-第二十二齿轮、23-第一KV离合器、24-第二十四齿轮、25-第二十五齿轮、26-第二十六齿轮、27-第一KR离合器、28-第二十八齿轮、29-第二十九齿轮、30-主输入轴、31-主输出轴、32-作业泵。
具体实施方式
下面结合本发明实施例中的附图，对本发明实施例中技术方案进行详细的描述，显然，所描述的实施例仅是本发明一部分实施例，而不是全部的实施例；基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例都属于本发明保护的范围。
如图1所示，本发明的工程机械用三段式机械复合无级传动装置，包括壳体1、主输入轴30、主输出轴31、液压泵2和液压马达20；所述主输入轴30一端与工程机械的发动机组动力连接，所述主输入轴30另一端动力连接一作业泵32，所述主输入轴30贯穿所述壳体1并与所述壳体1活动连接，所述主输入轴30上固定设置有一第五齿轮5；所述主输出轴31用于为工程机械的行走、作业和转向输出动力，所述主输出轴31与所述壳体1活动连接，所述主输出轴31上固定设置有一第二十九齿轮29；所述液压泵2的动力输入轴与所述壳体1活动连接，所述液压泵2的动力 输入轴位于所述壳体1内的部分固定设置有一第四齿轮4，所述第四齿轮4与所述第五齿轮5相啮合；所述液压马达20的动力输出轴与所述壳体1活动连接，所述液压马达20的动力输出轴位于所述壳体1内的部分固定设置有一第二十二齿轮22；所述液压泵2与所述液压马达20组成闭式液压回路；还包括第一半轴，所述第一半轴一端与所述壳体1活动连接，另一端固定设置有一第八太阳轮8，所述第一半轴上设置有一第六齿轮6，所述第六齿轮6与所述第五齿轮5相啮合；还包括第二半轴，所述第二半轴与所述第一半轴同轴设置，所述第二半轴一端与所述壳体1活动连接，另一端固定设置有一第十太阳轮10；所述第二半轴上设置有一第一K2离合器16以及一第一K3离合器18，所述第二半轴上转动设置有第十七齿轮17和第十五齿轮15，所述第十七齿轮17与所述第一K3离合器18的主动端动力连接，所述第十五齿轮15与所述第一K2离合器16的主动端动力连接；还包括第十一行星架11，所述第十一行星架11上设置有多个第七行星轮7和多个第九行星轮9，所述第七行星轮7与所述第八太阳轮8动力连接，所述第九行星轮9与所述第十太阳轮10动力连接；所述第十一行星架11固定连接有一第一K1离合器14，所述第一K1离合器14的主动端与所述第十五齿轮15动力连接；还包括一第一中间轴，所述第一中间轴设置于所述壳体1内并与所述壳体1活动连接，所述第一中间轴上活动设置有一第十九齿轮19以及一第二十一齿轮21，所述第十九齿轮19与所述第二十二齿轮22相啮合，所述第第二十一齿轮21与所述第十五齿轮15相啮合，所述第一中间轴上固定设置有一第二十四齿轮24以及一第二十五齿轮25，所述第二十四齿轮24与所述第十七齿轮17相啮合，所述第二十五齿轮25与所述第二十九齿轮29相啮合，所述第一中间轴上还设置有一第一KV离合器23，所述第一KV离合器23的主动端与所述第二十一齿轮21相啮合；还包括第二中间轴、第二十八齿轮28和第二十六齿轮26，所述第二十八齿轮28固定设置于所述第二中间轴上，所述第二十六齿轮26转动设置于所述第二中间轴上，所述第二十八齿轮28与所述第二十九齿轮29相啮合，所述第二中间轴上还设置有一第一KR离合器27，所述第一KR离合器27的主动端与所述第二十六齿轮26相啮合；还包括同轴固定设置的第十二齿轮12和第十三齿轮13，所述第 十二齿轮12与所述第九齿轮相啮合，所述第十三齿轮13与所述第十九齿轮19相啮合；还包括补油泵3，所述补油泵3与所述液压泵2动力连接，为整车提供工作和转向所需的油压。
本发明中的工程机械用三段式机械复合无级传动装置，其换挡逻辑如下表所示(表示需要接合的离合器)：
Figure PCTCN2018082412-appb-000001
以工程机械的前进为例，进一步说明本发明中的工程机械用三段式机械复合无级传动装置的工作原理：
第一段为液压机械Ⅰ段，发动机输入功率通过主输入轴30输入，一方面，经第五齿轮5和第四齿轮4传递到液压泵2，液压泵2与液压马达20组成闭合回路，液压泵2转动使液压马达20同步转动，同时液压泵2带动补油泵3工作，为整车提供工作和转向所需的油压；另一方面，经第六齿轮6传递到第八太阳轮8。
此时，第一K1离合器14和第一KV离合器23均接合，第八太阳轮8上的功率经第七行星轮7和第九行星轮9传递到第一K1离合器14，第一K1离合器14驱动第十五齿轮15，功率通过第十五齿轮15、第二十一齿轮21和第一KV离合器23传递到第二十五齿轮25，再由第二十五齿轮25经第二十九齿轮29传递到主输出轴31。
第二段为液压机械Ⅱ段，当需要将档位由第一段换到第二段时，由于第七行星轮7、第八太阳轮8、第九行星轮9和第十太阳轮10形成的差速结构，可以先接合第一K2离合器16，再分离第一K1离合器14，以保证动力的不中断输出，提高作业效率。
具体的，发动机输入功率通过主输入轴30输入，一方面，经第五齿轮5和第四齿轮4传递到液压泵2，液压泵2与液压马达20组成闭合回路，液压泵2转动使液压马达20同步转动，同时液压泵2带动补油泵3工作，为整车提供工作和转向所需的油压；另一方面，经第六齿轮6传递 到第八太阳轮8，第八太阳轮8上的功率经第七行星轮7和第九行星轮9传递到第十太阳轮10，再经过第一K2离合器16、第十五齿轮15、第二十一齿轮21、第一KV离合器23传递到第二十五齿轮25，再由第二十五齿轮25经第二十九齿轮29传递到主输出轴31。
第三段为液压机械Ⅲ段，此时，只有第一K3离合器18接合，发动机输入功率通过主输入轴30输入，一方面，经第五齿轮5和第四齿轮4传递到液压泵2，液压泵2与液压马达20组成闭合回路，液压泵2转动使液压马达20同步转动，同时液压泵2带动补油泵3工作，为整车提供工作和转向所需的油压；另一方面，经第六齿轮6传递到第八太阳轮8，第八太阳轮8上的功率经第七行星轮7和第九行星轮9传递到第十太阳轮10，再经过第一K3离合器18、第十七齿轮17、第二十四齿轮24和第二十九齿轮29传递到主输出轴31。
上述三段档位中，发动机传入的功率，均通过一机械路和一液压路传递，机械路即为各齿轮与离合器间的功率传递，液压路即为液压泵2和液压马达20穿入第二十二齿轮22，再经过第十九齿轮19、第十三齿轮13和第十二齿轮12传递到第九齿轮，大部分功率通过机械路传递，液压路只传递少部分功率，实现了高传递效率及无级变速，达到了提高作业效率、降低发动机油耗的技术效果。
图2为液压泵2、变量马达转速图，图中，曲线1为纯液压段变量马达转速，曲线2为液压机械Ⅰ段变量马达转速，曲线3为液压机械Ⅱ段变量马达转速，曲线4为液压泵2的转速。
图3为本发明的液压泵2最大压力图，图中，曲线1表示纯液压段的液压泵2工作压力，曲线2表示液压机械Ⅰ段的液压泵2工作压力，曲线3表示液压机械Ⅱ段的液压泵2工作压力。
图4为本发明的最大输出转矩图，图中，曲线1表示纯液压段的最大输出转矩，曲线2表示液压机械Ⅰ段的最大输出转矩，曲线3表示液压机械Ⅱ段的最大输出转矩。
图5为本发明的效率图，图中，实线1为液压机械Ⅰ段的效率曲线，实线2为液压机械Ⅱ段的效率曲线，实线3为液压机械Ⅲ段的效率曲线，虚线为装载机传统四挡液力机械动力换挡变速箱的效率曲线。
上面结合附图对本发明的实施方式作了详细说明，但是本发明并不限于上述实施方式，在所属技术领域普通技术人员所具备的知识范围内，还可以在不脱离本发明宗旨的前提下作出各种变化。

Claims (2)

  1. 一种工程机械用三段式机械复合无级传动装置，其特征在于：包括壳体、主输入轴、主输出轴、液压泵和液压马达；
    所述主输入轴一端与工程机械的发动机组动力连接，所述主输入轴另一端动力连接一作业泵，所述主输入轴贯穿所述壳体并与所述壳体活动连接，所述主输入轴上固定设置有一第五齿轮；
    所述主输出轴用于为工程机械的行走、作业和转向输出动力，所述主输出轴与所述壳体活动连接，所述主输出轴上固定设置有一第二十九齿轮；
    所述液压泵的动力输入轴与所述壳体活动连接，所述液压泵的动力输入轴位于所述壳体内的部分固定设置有一第四齿轮，所述第四齿轮与所述第五齿轮相啮合；
    所述液压马达的动力输出轴与所述壳体活动连接，所述液压马达的动力输出轴位于所述壳体内的部分固定设置有一第二十二齿轮；
    所述液压泵与所述液压马达组成闭式液压回路；
    还包括第一半轴，所述第一半轴一端与所述壳体活动连接，另一端固定设置有一第八太阳轮，所述第一半轴上设置有一第六齿轮，所述第六齿轮与所述第五齿轮相啮合；
    还包括第二半轴，所述第二半轴与所述第一半轴同轴设置，所述第二半轴一端与所述壳体活动连接，另一端固定设置有一第十太阳轮；所述第二半轴上设置有一第一K2离合器以及一第一K3离合器，所述第二半轴上转动设置有第十七齿轮和第十五齿轮，所述第十七齿轮与所述第一K3离合器的主动端动力连接，所述第十五齿轮与所述第一K2离合器的主动端动力连接；
    还包括第十一行星架，所述第十一行星架上设置有多个第七行星轮和多个第九行星轮，所述第七行星轮与所述第八太阳轮动力连接，所述第九行星轮与所述第十太阳轮动力连接；
    所述第十一行星架固定连接有一第一K1离合器，所述第一K1离合器的主动端与所述第十五齿轮动力连接；
    还包括一第一中间轴，所述第一中间轴设置于所述壳体内并与所述壳体活动连接，所述第一中间轴上活动设置有一第十九齿轮以及一第二十一 齿轮，所述第十九齿轮与所述第二十二齿轮相啮合，所述第第二十一齿轮与所述第十五齿轮相啮合，所述第一中间轴上固定设置有一第二十四齿轮以及一第二十五齿轮，所述第二十四齿轮与所述第十七齿轮相啮合，所述第二十五齿轮与所述第二十九齿轮相啮合，所述第一中间轴上还设置有一第一KV离合器，所述第一KV离合器的主动端与所述第二十一齿轮相啮合；
    还包括第二中间轴、第二十八齿轮和第二十六齿轮，所述第二十八齿轮固定设置于所述第二中间轴上，所述第二十六齿轮转动设置于所述第二中间轴上，所述第二十八齿轮与所述第二十九齿轮相啮合，所述第二中间轴上还设置有一第一KR离合器，所述第一KR离合器的主动端与所述第二十六齿轮相啮合；
    还包括同轴固定设置的第十二齿轮和第十三齿轮，所述第十二齿轮与所述第九齿轮相啮合，所述第十三齿轮与所述第十九齿轮相啮合。
  2. 如权利要求1所述的一种工程机械用三段式机械复合无级传动装置，其特征在于：还包括补油泵，所述补油泵与所述液压泵动力连接。
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