CN114877040A - Mechanical hydraulic planetary cone ring composite transmission device and control method thereof - Google Patents

Mechanical hydraulic planetary cone ring composite transmission device and control method thereof Download PDF

Info

Publication number
CN114877040A
CN114877040A CN202210568748.6A CN202210568748A CN114877040A CN 114877040 A CN114877040 A CN 114877040A CN 202210568748 A CN202210568748 A CN 202210568748A CN 114877040 A CN114877040 A CN 114877040A
Authority
CN
China
Prior art keywords
gear
clutch
transmission
hydraulic
planetary
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202210568748.6A
Other languages
Chinese (zh)
Inventor
王东青
朱镇
杨彦朋
后睿
张奕涵
王富凯
董吴
徐书雷
史金钟
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Luoyang Tractor Research Institute Co ltd
Original Assignee
Luoyang Tractor Research Institute Co ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Luoyang Tractor Research Institute Co ltd filed Critical Luoyang Tractor Research Institute Co ltd
Priority to CN202210568748.6A priority Critical patent/CN114877040A/en
Publication of CN114877040A publication Critical patent/CN114877040A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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
    • 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
    • F16H2200/2056—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with ten engaging means

Landscapes

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

Abstract

The invention discloses a mechanical hydraulic planetary cone ring compound transmission device and a control method thereof, wherein the mechanical hydraulic planetary cone ring compound transmission device comprises an input assembly, a front planetary gear assembly, a planetary cone ring type stepless speed change transmission assembly, a rear planetary gear assembly, a hydraulic transmission assembly and an output shaft, and switching of a single-flow transmission mode and a compound transmission mode is realized by adjusting the transmission ratio of the planetary cone ring type stepless speed change transmission assembly, adjusting the displacement ratio of the hydraulic transmission assembly and controlling the joint switching between a clutch and a brake. Has the advantages that: the technical scheme of the invention can meet the operation requirement of engineering machinery under complex working conditions, improve the power utilization rate of the engine and improve the fuel economy; meanwhile, the device works stably, the speed regulation range is widened, the hydraulic transmission starts quickly, the speed can be changed and reversed quickly and without impact, the transmission ratio of the planetary cone ring type continuously variable transmission can be changed continuously, the transmission process is stable, and the temperature rise is low due to the low rotating speed of each element in the transmission, so that the service life is long.

Description

Mechanical hydraulic planetary cone ring composite transmission device and control method thereof
Technical Field
The invention relates to a transmission device and a control method thereof, in particular to a composite transmission device with three transmission modes of machinery, hydraulic pressure and a planetary cone ring and a control method thereof, belonging to the technical field of variable-speed transmission devices.
Background
With the high-speed development of economy in China, the construction of cities and key projects is accelerated, so that the engineering machinery has larger market and development space than before.
The transmission device plays a role in transmitting power and changing the running condition of the automobile. The working condition of the transmission directly influences evaluation indexes such as dynamic property, fuel economy, operation stability and the like of the automobile. For engineering machinery, because the working environment is complex and changeable, the working condition of an engine is changed greatly in the working process, and the running speed of the machinery is changed frequently, a transmission device is required to change the output of rotating speed and torque timely according to the actual load.
The walking driving system applied to engineering machinery at present usually adopts mechanical transmission, hydraulic transmission and mechanical-hydraulic composite transmission; although the mechanical transmission has high transmission efficiency, only a fixed transmission ratio exists, and frequent gear shifting is needed in the operation process; the hydraulic transmission can realize the function of stepless speed regulation and has the capacity of transmitting larger torque, but the transmission efficiency is low; the mechanical-hydraulic compound transmission has the advantages of two single-flow transmissions, and has stepless speed regulation performance, higher transmission efficiency and higher requirement on a hydraulic transmission system; the output torque and power of the planetary cone ring type stepless speed change transmission are changed along with the change of the output revolution, the planetary cone ring type stepless speed change transmission has the mechanical characteristics of variable torque and variable power, has stronger universality, simpler and more compact structure and process, has the advantages of stable speed change, reliable work and the like, and the transmission of the planetary cone ring type stepless speed change transmission depends on friction force, so that the applicable power range is narrower and the efficiency is lower.
The prior art only relates to the design of a single transmission device and a compound transmission device with two single transmission modes connected in parallel, and can not completely meet the design requirements of multiple modes, especially multiple compound modes, of the transmission device under different working conditions of engineering machinery.
Disclosure of Invention
The purpose of the invention is as follows: aiming at the defects in the prior art, the invention provides a mechanical hydraulic planetary cone ring composite transmission device and a control method thereof.
The technical scheme is as follows: a mechanical hydraulic planetary cone ring compound transmission device comprises:
an input assembly including an input shaft, a first gear pair, and a fourth clutch C 4 ；
The front planetary gear assembly comprises a front planetary gear ring gear and a fifth clutch C 5 The front planetary gear planet carrier, the front planetary gear sun gear, the brake B, the second gear pair and the front planetary gear output shaft, wherein the input shaft passes through a fourth clutch C 4 Is connected with the front planetary gear ring which passes through a fifth clutch C 5 The front planetary gear carrier is connected with a front planetary gear output shaft, and the brake B can lock a front planetary gear sun gear;
planetary cone ring type stepless speed change transmission assembly and sixth clutch C 6 Seventh clutch C 7 A third gear pair, a planet cone ring type continuously variable transmission input shaft, a planet cone ring type continuously variable transmission output shaft, an intermediate transmission shaft and a fourth gear pairGear pair, eighth clutch C 8 Ninth clutch C 9 The third gear pair is connected with the fourth gear pair through an intermediate transmission shaft, an output gear of the fourth gear pair is sleeved on an output shaft of the planetary cone ring type continuously variable transmission through an output gear shaft, and an input shaft of the planetary cone ring type continuously variable transmission is sleeved on an output shaft of the planetary cone ring type continuously variable transmission through a sixth clutch C 6 Is connected with the output shaft of the front planetary gear, and the third gear pair is connected with the output shaft of the front planetary gear through a seventh clutch C 7 The planetary cone ring type continuously variable transmission input shaft is connected with the planetary cone ring type continuously variable transmission output shaft through the planetary cone ring type continuously variable transmission;
the rear planetary gear assembly comprises a rear planetary gear ring gear, a rear planetary gear sun gear, a rear planetary gear planet carrier and a tenth clutch C 10 The planetary gear ring passes through a tenth clutch C 10 Is connected with a rear planet gear carrier which passes through an eighth clutch C 8 Connected with a fourth gear pair, and the sun gear of the rear planet gear passes through a ninth clutch C 9 The planetary cone ring type continuously variable transmission is connected with an output shaft of the planetary cone ring type continuously variable transmission;
a hydraulic transmission assembly including a hydraulic transmission input shaft, a first clutch C 1 Variable displacement pump, fixed displacement motor, hydraulic transmission output shaft and second clutch C 2 A third clutch C 3 The input shaft passes through a first gear pair and a first clutch C 1 The hydraulic transmission input shaft is connected with the variable pump, the variable pump drives the quantitative motor to work, the output end of the quantitative motor is connected with the hydraulic transmission output shaft, and the hydraulic transmission output shaft passes through the second clutch C 2 The second gear pair is connected with the sun gear of the front planetary gear, and the hydraulic transmission output shaft passes through a third clutch C 3 The fifth gear pair is connected with the rear planet gear carrier;
and the output shaft is connected with the rear planetary gear ring gear.
A control method of a mechanical hydraulic planetary cone ring compound transmission device realizes the switching of a single-flow transmission mode and a compound transmission mode by adjusting the transmission ratio of a planetary cone ring type stepless speed change transmission assembly, adjusting the displacement ratio of a hydraulic transmission assembly and controlling the joint switching between a clutch and a brake B; the single-flow transmission mode comprises a mechanical transmission mode, a hydraulic transmission mode and a planetary cone ring type stepless speed change transmission mode; the compound transmission modes comprise a mechanical-hydraulic compound transmission mode, a mechanical-planetary cone ring compound transmission mode, a hydraulic-planetary cone ring compound transmission mode and a mechanical-hydraulic-planetary cone ring compound transmission mode.
Preferably, the hydraulic-planetary cone ring compound transmission mode comprises a hydraulic-planetary cone ring parallel compound transmission mode and a hydraulic-planetary cone ring series compound transmission mode.
The engagement elements for each transmission mode are shown in table 1, specifically as follows:
TABLE 1 Transmission mode switching element engagement status
Figure BDA0003658277480000021
Figure BDA0003658277480000031
Preferably, the control method of the single-flow transmission mode comprises the following steps:
the hydraulic transmission modes are divided into a hydraulic transmission H1 transmission mode and a hydraulic transmission H2 transmission mode,
hydraulic transmission H1 transmission mode: first clutch C 1 A third clutch C 3 And a tenth clutch C 10 Engaging while the second clutch C 2 And a fourth clutch C 4 Fifth clutch C 5 Sixth clutch C 6 Seventh clutch C 7 Eighth clutch C 8 Ninth clutch C 9 The brake B is separated, power is transmitted to the hydraulic transmission input shaft from the input shaft through the first gear pair to drive the variable pump to work, the variable pump outputs high-pressure oil to drive the quantitative motor to rotate, and the power output by the output end of the quantitative motor is output through hydraulic transmissionThe shaft and the fifth gear pair are transmitted to a rear planetary gear carrier, the rear planetary gear assembly is fixedly connected into a whole, and power is transmitted to an output shaft through the rear planetary gear assembly to be output;
hydraulic transmission H2 transmission mode: first clutch C 1 A second clutch C 2 Fifth clutch C 5 Seventh clutch C 7 Eighth clutch C 8 And a tenth clutch C 10 Engaging while the third clutch C 3 And a fourth clutch C 4 Sixth clutch C 6 Ninth clutch C 9 The power is transmitted to the hydraulic transmission input shaft from the input shaft through the first gear pair to drive the variable pump to work, the variable pump outputs high-pressure oil to drive the quantitative motor to rotate, the power output by the output end of the quantitative motor is transmitted to the front planetary gear sun gear through the hydraulic transmission output shaft and the second gear pair, the front planetary gear assembly and the rear planetary gear assembly are respectively and fixedly connected into a whole, the power is transmitted to the rear planetary gear planet carrier through the third gear pair, the middle transmission shaft and the fourth gear pair, and the power is transmitted to the output shaft through the rear planetary gear assembly to be output;
mechanical transmission mode: fourth clutch C 4 Seventh clutch C 7 Eighth clutch C 8 Tenth clutch C 10 And brake B while the first clutch C is engaged 1 A second clutch C 2 A third clutch C 3 Fifth clutch C 5 Sixth clutch C 6 And a ninth clutch C 9 Separated, the power passes through the fourth clutch C from the input shaft 4 The front planetary gear ring is driven to work, and the power output by the front planetary gear ring passes through the front planetary gear planet carrier, the front planetary gear output shaft and the seventh clutch C 7 A third gear pair, an intermediate transmission shaft, a fourth gear pair and an eighth clutch C 8 The power is transmitted to a rear planetary gear carrier, the rear planetary gear assembly is fixedly connected into a whole, and the power is transmitted to an output shaft through the rear planetary gear assembly to be output;
planetary cone ring type stepless speed change transmission mode: fourth clutch C 4 Fifth clutch C 5 Sixth clutch C 6 Ninth clutch C 9 And a tenth clutch C 10 Engaging while the first clutch C is engaged 1 And a second clutch C 2 A third clutch C 3 Seventh clutch C 7 Eighth clutch C 8 And the brake B is separated, power is transmitted to a front planetary gear ring by an input shaft, the front planetary gear assembly is fixedly connected into a whole, the power is transmitted to the planetary cone ring type continuously variable transmission input shaft through the front planetary gear assembly to drive the planetary cone ring type continuously variable transmission to work, the power output by the planetary cone ring type continuously variable transmission is transmitted to a rear planetary gear sun gear through a planetary cone ring type continuously variable transmission output shaft, the rear planetary gear assembly is fixedly connected into a whole, and the power is transmitted to an output shaft through the rear planetary gear assembly to be output.
Preferably, the control method of the compound transmission mode is as follows:
mechanical-hydraulic compound transmission mode: first clutch C 1 A second clutch C 2 And a fourth clutch C 4 Seventh clutch C 7 Eighth clutch C 8 And a tenth clutch C 10 Engaging while the third clutch C 3 Fifth clutch C 5 Sixth clutch C 6 Ninth clutch C 9 And brake B, power split at the input shaft: one path of power is transmitted to a front planetary gear ring, the other path of power is transmitted to a hydraulic transmission input shaft through a first gear pair to drive a variable pump to work, the variable pump outputs high-pressure oil to drive a quantitative motor to rotate, the power output by the output end of the quantitative motor is transmitted to a front planetary gear sun gear through a hydraulic transmission output shaft and a second gear pair, the power transmitted to the front planetary gear ring and the power transmitted to the front planetary gear sun gear are converged at a front planetary gear carrier and then transmitted to a rear planetary gear carrier through a front planetary gear output shaft, a third gear pair, a middle transmission shaft and a fourth gear pair, the rear planetary gear assembly is fixedly connected into a whole, and the power is transmitted to the output shaft through the rear planetary gear assembly to be output;
mechanical-planetary cone ring compound transmission mode: fourth clutch C 4 Fifth clutch C 5 Sixth clutch C 6 Seventh clutch C 7 Eighth clutch C 8 And a ninth clutch C 9 Engaging while the first clutch C is engaged 1 A second clutch C 2 A third clutch C 3 Tenth clutch C 10 And the brake B is separated, the front planetary gear assembly is fixedly connected into a whole, and power is transmitted to the front planetary gear assembly through the input shaft to be shunted: one path of power is transmitted to a rear planet gear carrier through a front planet gear output shaft, a third gear pair, a middle transmission shaft and a fourth gear pair, the other path of power drives a planet cone ring type continuously variable transmission to work through a planet cone ring type continuously variable transmission input shaft, the power output by the planet cone ring type continuously variable transmission is transmitted to a rear planet gear sun gear through the planet cone ring type continuously variable transmission output shaft, and the power transmitted to the rear planet gear carrier and the power transmitted to the rear planet gear sun gear are converged at a rear planet gear ring gear and then transmitted to the output shaft for output;
the hydraulic-planetary conical ring compound transmission mode is divided into a hydraulic-planetary conical ring parallel compound transmission mode and a hydraulic-planetary conical ring series compound transmission mode;
the hydraulic-planet conical ring parallel composite transmission mode is as follows: first clutch C 1 And a third clutch C 3 And a fourth clutch C 4 Fifth clutch C 5 Sixth clutch C 6 And a ninth clutch C 9 Engaging while the second clutch C 2 Seventh clutch C 7 Eighth clutch C 8 Tenth clutch C 10 And the brake B is separated, the front planetary gear assembly is fixedly connected into a whole, and power is divided at the input shaft: power transmits to hydraulic drive input shaft drive variable pump work through first gear pair all the way, variable pump output high pressure fluid drive constant displacement motor is rotatory, the power of constant displacement motor output passes through hydraulic drive output shaft, the vice transmission of fifth gear to back planet gear planet carrier, and another way power transmits to planet cone ring formula buncher work through preceding planetary gear assembly, planet cone ring formula buncher drive planet cone ring formula buncher of planet cone ring formula, planet cone ring formula buncher workThe power output by the device is transmitted to a rear planetary gear sun gear through an output shaft of the planetary cone ring type continuously variable transmission, and the power transmitted to a rear planetary gear carrier and the power transmitted to the rear planetary gear sun gear are converged at a rear planetary gear ring gear and then transmitted to the output shaft for output;
the hydraulic-planet conical ring series composite transmission mode is as follows: first clutch C 1 A second clutch C 2 Fifth clutch C 5 Sixth clutch C 6 Ninth clutch C 9 And a tenth clutch C 10 Engaging while the third clutch C 3 And a fourth clutch C 4 Seventh clutch C 7 Eighth clutch C 8 The power is transmitted to a hydraulic transmission input shaft from an input shaft through a first gear pair to drive a variable pump to work, the variable pump outputs high-pressure oil to drive a quantitative motor to rotate, the power output by the output end of the quantitative motor is transmitted to a front planetary gear sun gear through a hydraulic transmission output shaft and a second gear pair, the front planetary gear assembly is fixedly connected into a whole, the power is transmitted to a planetary cone ring type stepless transmission input shaft through the front planetary gear assembly to drive a planetary cone ring type stepless transmission to work, the power output by the planetary cone ring type stepless transmission is transmitted to a rear planetary gear sun gear through the planetary cone ring type stepless transmission output shaft, the rear planetary gear assembly is fixedly connected into a whole, and the power is transmitted to an output shaft through the rear planetary gear assembly to be output;
mechanical-hydraulic-planet cone ring compound transmission mode: first clutch C 1 A second clutch C 2 And a fourth clutch C 4 Sixth clutch C 6 Ninth clutch C 9 And a tenth clutch C 10 Engaging while the third clutch C 3 Fifth clutch C 5 Seventh clutch C 7 Eighth clutch C 8 And brake B, power split at the input shaft: power transmission is to preceding planetary gear tooth circle all the way, and another way power transmits to hydraulic drive input shaft drive variable pump work through first gear pair, variable pump output high pressure fluid drive ration motor is rotatory, the power of ration motor outputThrough hydraulic transmission output shaft, the vice transmission of second gear to preceding planetary gear sun gear, the power of transmission to preceding planetary gear tooth circle joins the back through planet cone ring formula buncher input shaft drive planet cone ring formula buncher work at preceding planetary gear planet carrier department with the power of transmission to preceding planetary gear sun gear, the power of planet cone ring formula buncher output passes through planet cone ring formula buncher output shaft and transmits to back planetary gear sun gear, back planetary gear subassembly links firmly as an organic whole, and power transmits to output shaft output through back planetary gear subassembly.
Preferably, the output shaft speed n of the single-flow transmission mode o The calculation method is as follows:
the hydraulic transmission modes are divided into a hydraulic transmission H1 transmission mode and a hydraulic transmission H2 transmission mode,
hydraulic transmission H1 transmission mode:
Figure BDA0003658277480000061
in the formula, n o Is the output shaft speed, n I For input shaft speed, e is the displacement ratio of the hydrostatic transmission assembly, i 1 Is the gear ratio of the first gear pair i 5 The transmission ratio of the fifth gear pair;
hydraulic transmission H2 transmission mode:
Figure BDA0003658277480000062
in the formula, n o Is the output shaft speed, n I For input shaft speed, e is the displacement ratio of the hydrostatic transmission assembly, i 1 Is the gear ratio of the first gear pair i 2 Is the gear ratio of the second gear pair, i 3 Is the gear ratio of the third gear pair, i 4 The transmission ratio of the fourth gear pair;
mechanical transmission mode:
Figure BDA0003658277480000063
in the formula, n o Is the output shaft speed, n I As input shaft speed, k 1 Characteristic parameter of planet gear of front planet gear assembly, i 3 Is the gear ratio of the third gear pair, i 4 The transmission ratio of the fourth gear pair;
planetary cone ring type stepless speed change transmission mode:
Figure BDA0003658277480000064
in the formula, n o Is the output shaft speed, n I As input shaft speed, i k The transmission ratio of the planetary cone ring type continuously variable transmission assembly is shown.
Preferably, the output shaft speed n of the compound transmission mode o The calculation method is as follows:
mechanical-hydraulic compound transmission mode:
Figure BDA0003658277480000065
in the formula, n o Is the output shaft speed, n I Is the input shaft speed, e is the displacement ratio of the hydrostatic transmission assembly, k 1 Characteristic parameter of planet gear of front planet gear assembly, i 1 Is the gear ratio of the first gear pair i 2 Is the gear ratio of the second gear pair, i 3 Is the gear ratio of the third gear pair, i 4 The transmission ratio of the fourth gear pair;
mechanical-planetary cone ring compound transmission mode:
Figure BDA0003658277480000071
in the formula, n o Is the output shaft speed, n I As input shaft speed, k 2 Is a characteristic parameter of the planet gears of the rear planetary gear assembly, i k Is a planet cone ringTransmission ratio of infinitely variable transmission assembly, i 2 Is the gear ratio of the second gear pair, i 3 Is the gear ratio of the third gear pair, i 4 The transmission ratio of the fourth gear pair;
the hydraulic-planetary conical ring compound transmission mode is divided into a hydraulic-planetary conical ring parallel compound transmission mode and a hydraulic-planetary conical ring series compound transmission mode;
the hydraulic-planet conical ring parallel composite transmission mode is as follows:
Figure BDA0003658277480000072
in the formula, n o Is the output shaft speed, n I As input shaft speed, k 2 Is a characteristic parameter of the planet gears of the rear planetary gear assembly, i k Ratio of a planetary cone-ring type continuously variable transmission assembly, i 1 Is the gear ratio of the first gear pair i 5 The transmission ratio of the fifth gear pair;
the hydraulic-planet conical ring series composite transmission mode is as follows:
Figure BDA0003658277480000073
in the formula, n o Is the output shaft speed, n I For input shaft speed, e is the displacement ratio of the hydrostatic transmission assembly, i k Ratio of a planetary cone-ring type continuously variable transmission assembly, i 1 Is the gear ratio of the first gear pair i 2 Is the gear ratio of the second gear pair;
mechanical-hydraulic-planet cone ring compound transmission mode:
Figure BDA0003658277480000074
in the formula, n o Is the output shaft speed, n I Is the input shaft speed, e is the displacement ratio of the hydrostatic transmission assembly, k 1 Characteristic parameter of planet gear of front planet gear assembly, i k Ratio of a planetary cone-ring type continuously variable transmission assembly, i 1 Is the gear ratio of the first gear pair i 2 The gear ratio of the second gear pair.
Preferably, stepless speed regulation switching among the multiple transmission modes is realized by adjusting the transmission ratio of the planetary cone ring type stepless speed change transmission assembly, adjusting the displacement ratio of the hydraulic transmission assembly and controlling the engagement between the clutch and the brake B.
Preferably, the transmission modes involved in the stepless speed regulation switching among the plurality of transmission modes are as follows:
"Hydraulic Transmission H1 Transmission mode" - "Hydraulic Transmission H2 Transmission mode" - "mechanical Transmission mode" - "Planet Cone Ring type continuously variable Transmission mode" -;
the transmission mode comprises a mechanical-hydraulic compound transmission mode, a mechanical-planetary cone ring compound transmission mode, a hydraulic-planetary cone ring parallel compound transmission mode, a hydraulic-planetary cone ring series compound transmission mode and a mechanical-hydraulic-planetary cone ring compound transmission mode.
Has the advantages that: the invention realizes the switching of a mechanical transmission mode, a hydraulic transmission mode, a planetary cone ring type stepless speed change transmission mode, a mechanical-hydraulic composite transmission mode, a mechanical-planetary cone ring composite transmission mode, a hydraulic-planetary cone ring parallel composite transmission mode, a hydraulic-planetary cone ring series composite transmission mode and a mechanical-hydraulic-planetary cone ring composite transmission mode by adjusting the transmission ratio of the planetary cone ring type stepless speed change transmission component, adjusting the displacement ratio of the hydraulic transmission component and controlling the joint switching between the clutch and the brake, thereby meeting the operation requirement of complex working conditions of engineering machinery, improving the power utilization rate of an engine and improving the fuel economy; meanwhile, the device works stably, the speed regulation range is widened, the hydraulic transmission starts quickly, the speed can be changed and reversed quickly and without impact, the transmission ratio of the planetary cone ring type continuously variable transmission can be changed continuously, the transmission process is stable, and the temperature rise is low due to the low rotating speed of each element in the transmission, so that the service life is long.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the provided drawings without creative efforts.
Fig. 1 is a schematic diagram of the structure of the present invention.
FIG. 2 is a power flow diagram of the hydraulic transmission H1 transmission mode of the present invention.
FIG. 3 is a power flow diagram of the hydraulic transmission H2 transmission mode of the present invention.
FIG. 4 is a power flow diagram of the mechanical drive mode of the present invention.
FIG. 5 is a power flow diagram of a planetary cone-ring continuously variable transmission mode of the present invention.
FIG. 6 is a power flow schematic of the mechanical-hydraulic compound transmission mode of the present invention.
FIG. 7 is a power flow diagram of the mechanical-planetary cone ring compound transmission mode of the present invention.
FIG. 8 is a power flow diagram of a compound hydraulic-planetary cone ring parallel transmission mode of the present invention.
FIG. 9 is a power flow diagram of a hydro-planetary cone ring series compound transmission mode of the present invention.
FIG. 10 is a power flow schematic of the Mechanical-Hydraulic-Planet Cone Ring compound drive mode of the present invention.
FIG. 11 is a plot of output speed versus input speed for a single flow transmission mode of the present invention.
FIG. 12 is a graph of output speed versus input speed for the compound transmission mode of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. "beneath," "under" and "beneath" a first feature includes the first feature being directly beneath and obliquely beneath the second feature, or simply indicating that the first feature is at a lesser elevation than the second feature.
As shown in fig. 1, a mechanical hydraulic planetary cone ring compound transmission device includes:
an input assembly 1 including an input shaft 11, a first gear pair 12, and a fourth clutch C 4 13；
The front planetary gear assembly 2 comprises a front planetary gear ring gear 21 and a fifth clutch C 5 22. A front planetary gear carrier 23, a front planetary gear sun gear 24, a brake B25, a second gear pair 26 and a front planetary gear output shaft 27, wherein the input shaft 11 passes through a fourth clutch C 4 13 is connected to a front planetary gear ring 21, said front planetary gear ring 21 being connected via a fifth clutch C 5 22 is connected to the front planet carrier 23, the front planet carrier 23 is connected to the front planet output shaft 27, and the brake B25 canTo lock the front planetary gear sun 24;
planetary cone ring type stepless speed change transmission assembly 3 and sixth clutch C 6 31. Seventh clutch C 7 32. Third gear pair 33, planetary cone ring type continuously variable transmission input shaft 34, planetary cone ring type continuously variable transmission 35, planetary cone ring type continuously variable transmission output shaft 36, intermediate transmission shaft 37, fourth gear pair 38 and eighth clutch C 8 39. Ninth clutch C 9 310. A fifth gear pair 311, the third gear pair 33 is connected with a fourth gear pair 38 through an intermediate transmission shaft 37, an output gear of the fourth gear pair 38 is sleeved on an output shaft 36 of the planetary cone ring type continuously variable transmission through an output gear sleeve, and an input shaft 34 of the planetary cone ring type continuously variable transmission is connected with a sixth clutch C 6 31 is connected to the front planetary gear output shaft 27, and the third gear pair 33 is connected via a seventh clutch C 7 32 is connected with a front planetary gear output shaft 27, and the planetary cone ring type continuously variable transmission input shaft 34 is connected with a planetary cone ring type continuously variable transmission output shaft 36 through a planetary cone ring type continuously variable transmission 35;
the rear planetary gear assembly 4 includes a rear planetary gear ring 41, a rear planetary gear sun gear 42, a rear planetary gear carrier 43, and a tenth clutch C 10 44, the star gear ring gear 41 passes through a tenth clutch C 10 44 is connected to a rear planet carrier 43, said rear planet carrier 43 being connected via an eighth clutch C 8 39 is connected to a fourth gear wheel pair 38, the rear planet wheel sun gear 42 being connected via a ninth clutch C 9 310 is connected with the output shaft 36 of the planetary cone ring type continuously variable transmission;
a hydraulic transmission assembly 5 comprising a hydraulic transmission input shaft 51, a first clutch C 1 52. Variable displacement pump 53, constant displacement motor 54, hydraulic transmission output shaft 55, second clutch C 2 56. Third clutch C 3 57, the input shaft 11 passes through the first gear pair 12 and the first clutch C 1 52 is connected with a hydraulic transmission input shaft 51, the hydraulic transmission input shaft 51 is connected with a variable pump 53, the variable pump 53 drives a fixed-displacement motor 54 to work, the output end of the fixed-displacement motor 54 is connected with a hydraulic transmission output shaft 55, and the hydraulic transmission output shaft 55 is communicated withSecond clutch C 2 56. The second gear pair 26 is connected to the front planetary sun gear 24, and the hydraulic drive output shaft 55 is connected via a third clutch C 3 57. The fifth gear pair 311 is connected to the rear planet carrier 43;
and the output shaft 6 is connected with the rear planetary gear ring gear 41.
The invention realizes the switching of a mechanical transmission mode, a hydraulic transmission mode, a planetary cone ring type stepless speed change transmission mode, a mechanical-hydraulic composite transmission mode, a mechanical-planetary cone ring composite transmission mode, a hydraulic-planetary cone ring parallel composite transmission mode, a hydraulic-planetary cone ring series composite transmission mode and a mechanical-hydraulic-planetary cone ring composite transmission mode by adjusting the transmission ratio of the planetary cone ring type stepless speed change transmission component 3, adjusting the displacement ratio of the hydraulic transmission component 5 and controlling the joint switching between the clutch and the brake, can meet the complex working condition operation requirement of engineering machinery, improve the power utilization rate of an engine and improve the fuel economy; meanwhile, the device works stably, the speed regulation range is widened, the hydraulic transmission starts quickly, the speed can be changed and reversed quickly and without impact, the transmission ratio of the planetary cone ring type continuously variable transmission can be changed continuously, the transmission process is stable, and the temperature rise is low due to the low rotating speed of each element in the transmission, so that the service life is long.
A control method of a mechanical hydraulic planetary cone ring compound transmission device realizes the switching of a single-flow transmission mode and a compound transmission mode by adjusting the transmission ratio of a planetary cone ring type stepless speed change transmission assembly 3, adjusting the displacement ratio of a hydraulic transmission assembly 5 and controlling the connection switching between a clutch and a brake B25; the single-flow transmission mode comprises a mechanical transmission mode, a hydraulic transmission mode and a planetary cone ring type stepless speed change transmission mode; the compound transmission modes comprise a mechanical-hydraulic compound transmission mode, a mechanical-planetary cone ring compound transmission mode, a hydraulic-planetary cone ring parallel compound transmission mode, a hydraulic-planetary cone ring series compound transmission mode and a mechanical-hydraulic-planetary cone ring compound transmission mode.
The engagement elements for each transmission mode are shown in table 1, specifically as follows:
TABLE 1 Transmission mode switching element engagement status
Figure BDA0003658277480000101
Figure BDA0003658277480000111
The hydraulic transmission modes are divided into a hydraulic transmission H1 transmission mode and a hydraulic transmission H2 transmission mode.
As shown in fig. 2, the control method of the transmission mode of the hydraulic transmission H1 is as follows:
first clutch C 1 52. Third clutch C 3 57 and tenth clutch C 10 44 are engaged while the second clutch C is engaged 2 56. Fourth clutch C 4 13. Fifth clutch C 5 22. Sixth clutch C 6 31. Seventh clutch C 7 32. Eighth clutch C 8 39. Ninth clutch C 9 310 and the separation of stopper B25, power is transmitted to hydraulic drive input shaft 51 through first gear pair 12 by input shaft 11 and is driven variable pump 53 and work, variable pump 53 outputs high-pressure fluid drive ration motor 54 and rotates, the power of ration motor 54 output passes through hydraulic drive output shaft 55, the transmission of fifth gear pair 311 to back planet carrier 43, back planetary gear assembly 4 links firmly as an organic whole, and power transmits to output shaft 6 through back planetary gear assembly 4 and exports.
The method for calculating the rotating speed of the output shaft 6 in the hydraulic transmission H1 transmission mode comprises the following steps:
Figure BDA0003658277480000112
in the formula, n o For the rotational speed of the output shaft 6, n I For the speed of rotation of the input shaft 11, e is the displacement ratio of the hydraulic transmission assembly 5, i 1 Is the gear ratio of the first gear pair 12, i 5 The gear ratio of the fifth gear pair 311.
As shown in FIG. 3, the control method for the transmission mode of the hydraulic transmission H2 is as follows:
first clutch C 1 52. Second clutch C 2 56. Fifth clutch C 5 22. Seventh clutch C 7 32. Eighth clutch C 8 39 and tenth clutch C 10 44 are engaged while the third clutch C is engaged 3 57. Fourth clutch C 4 13. Sixth clutch C 6 31. Ninth clutch C 9 310 and brake B25 separation, power is transmitted to hydraulic drive input shaft 51 through first gear pair 12 by input shaft 11 and is driven variable pump 53 and work, variable pump 53 outputs high-pressure fluid drive ration motor 54 and rotates, the power of ration motor 54 output end output passes through hydraulic drive output shaft 55, second gear pair 26 and transmits to preceding planetary gear sun gear 24, preceding planetary gear set 2 and back planetary gear set 4 link firmly as an organic whole respectively, and power transmits to back planetary gear planet carrier 43 through third gear pair 33, intermediate drive shaft 37, fourth gear pair 38, and power transmits to output shaft 6 through back planetary gear set 4 and exports.
The method for calculating the rotating speed of the output shaft 6 in the hydraulic transmission H2 transmission mode comprises the following steps:
Figure BDA0003658277480000121
in the formula, n o Is the rotational speed of the output shaft 6, n I For the speed of rotation of the input shaft 11, e is the displacement ratio of the hydraulic transmission assembly 5, i 1 Is the gear ratio of the first gear pair 12, i 2 Is the gear ratio of the second gear pair 26, i 3 Is the gear ratio of the third gear pair 33, i 4 The gear ratio of the fourth gear pair 38.
As shown in fig. 4, the control method of the mechanical transmission mode is as follows:
fourth clutch C 4 13. Seventh clutch C 7 32. Eighth clutch C 8 39. Tenth clutch C 10 44 and brake B25 are engaged while the first clutch C is engaged 1 52. Second clutch C 2 56. Third clutch C 3 57. Fifth clutch C 5 22. Sixth fromCombiner C 6 31 and a ninth clutch C 9 310 are disengaged and power is transmitted from the input shaft 11 through the fourth clutch C 4 13 drives the front planetary gear ring gear 21 to work, and the power output by the front planetary gear ring gear 21 passes through the front planetary gear carrier 23, the front planetary gear output shaft 27 and the seventh clutch C 7 32. Third gear pair 33, intermediate transmission shaft 37, fourth gear pair 38, eighth clutch C 8 39 to the rear planet gear carrier 43, the rear planet gear assembly 4 is fixedly connected into a whole, and the power is transmitted to the output shaft 6 through the rear planet gear assembly 4 to be output.
The method for calculating the rotating speed of the output shaft 6 in the mechanical transmission mode comprises the following steps:
Figure BDA0003658277480000122
in the formula, n o For the rotational speed of the output shaft 6, n I Is the rotational speed, k, of the input shaft 11 1 Is a characteristic parameter of the planet gears of the front planetary gear assembly 2, i 3 Is the gear ratio of the third gear pair 33, i 4 The gear ratio of fourth gear pair 38.
As shown in fig. 5, the control method of the planetary cone-ring type continuously variable transmission mode is as follows:
fourth clutch C 4 13. Fifth clutch C 5 22. Sixth clutch C 6 31. Ninth clutch C 9 310 and tenth clutch C 10 44 are engaged while the first clutch C is engaged 1 52. Second clutch C 2 56. Third clutch C 3 57. Seventh clutch C 7 32. Eighth clutch C 8 39 and brake B25 are separated, power is transmitted to the front planetary gear ring 21 by the input shaft 11, the front planetary gear assembly 2 is fixedly connected as a whole, the power is transmitted to the input shaft 34 of the planetary cone ring type continuously variable transmission to drive the planetary cone ring type continuously variable transmission 35 to work through the front planetary gear assembly 2, the power output by the planetary cone ring type continuously variable transmission 35 is transmitted to the rear planetary gear sun gear 42 through the output shaft 36 of the planetary cone ring type continuously variable transmission, the rear planetary gear assembly 4 is fixedly connected as a whole, and the power is transmitted through the rear planetary gearThe wheel assembly 4 transmits to the output shaft 6 for output.
The method for calculating the rotating speed of the output shaft 6 in the planetary cone ring type stepless speed change transmission mode comprises the following steps:
Figure BDA0003658277480000131
in the formula, n o For the rotational speed of the output shaft 6, n I For the rotational speed of the input shaft 11, i k The transmission ratio of the planetary cone ring type continuously variable transmission assembly 3.
As shown in fig. 6, the control method of the mechanical-hydraulic compound transmission mode is as follows:
first clutch C 1 52. Second clutch C 2 56. Fourth clutch C 4 13. Seventh clutch C 7 32. Eighth clutch C 8 39 and tenth clutch C 10 44 are engaged while the third clutch C is engaged 3 57. Fifth clutch C 5 22. Sixth clutch C 6 31. Ninth clutch C 9 310 and brake B25 are disengaged and power is split at the input shaft 11: one way power transmission is to preceding planetary gear ring gear 21, and another way power transmits to the work of hydraulic drive input shaft 51 drive variable pump 53 through first gear pair 12, variable pump 53 outputs high pressure fluid drive ration motor 54 and rotates, the power of ration motor 54 output passes through hydraulic drive output shaft 55, the transmission of second gear pair 26 to preceding planetary gear sun gear 24, and the power of transmission to preceding planetary gear ring gear 21 and the power of transmission to preceding planetary gear sun gear 24 pass through preceding planetary gear output shaft 27, third gear pair 33, intermediate drive shaft 37, the transmission of fourth gear pair 38 to back planetary gear carrier 43 after preceding planetary gear carrier 23 department joins, back planetary gear assembly 4 links firmly as an organic wholely, and power transmits to output shaft 6 through back planetary gear assembly 4 and exports.
The method for calculating the rotating speed of the output shaft 6 in the mechanical-hydraulic compound transmission mode comprises the following steps:
Figure BDA0003658277480000132
in the formula, n o Is the rotational speed of the output shaft 6, n I For the speed of rotation of the input shaft 11, e is the displacement ratio of the hydraulic transmission assembly 5, k 1 Is a characteristic parameter of the planet gears of the front planetary gear assembly 2, i 1 Is the gear ratio of the first gear pair 12, i 2 Is the gear ratio of the second gear pair 26, i 3 Is the gear ratio of the third gear pair 33, i 4 The gear ratio of fourth gear pair 38.
As shown in fig. 7, the control method of the mechanical-planetary cone ring compound transmission mode is as follows:
fourth clutch C 4 13. Fifth clutch C 5 22. Sixth clutch C 6 31. Seventh clutch C 7 32. Eighth clutch C 8 39 and ninth clutch C 9 310 are engaged while the first clutch C is engaged 1 52. Second clutch C 2 56. Third clutch C 3 57. Tenth clutch C 10 44 and a brake B25 are separated, the front planetary gear assembly 2 is fixedly connected into a whole, and power is transmitted to the front planetary gear assembly 2 through the input shaft 11 and is divided: one path of power is transmitted to the rear planet gear carrier 43 through the front planet gear output shaft 27, the third gear pair 33, the intermediate transmission shaft 37 and the fourth gear pair 38, the other path of power drives the planet cone ring type continuously variable transmission 35 to work through the planet cone ring type continuously variable transmission input shaft 34, the power output by the planet cone ring type continuously variable transmission 35 is transmitted to the rear planet gear sun gear 42 through the planet cone ring type continuously variable transmission output shaft 36, and the power transmitted to the rear planet gear carrier 43 and the power transmitted to the rear planet gear sun gear 42 are converged at the rear planet gear ring gear 41 and then transmitted to the output shaft 6 to be output.
The method for calculating the rotating speed of the output shaft 6 in the mechanical-planetary cone ring compound transmission mode comprises the following steps:
Figure BDA0003658277480000141
in the formula, n o For the rotational speed of the output shaft 6, n I Is the rotational speed, k, of the input shaft 11 2 To go backwardCharacteristic parameter of the planet gears of the planet gear assembly 4, i k Is the transmission ratio, i, of the planetary cone-ring continuously variable transmission assembly 3 2 Is the gear ratio of the second gear pair 26, i 3 Is the gear ratio of the third gear pair 33, i 4 The gear ratio of fourth gear pair 38.
As shown in fig. 8, the control method of the hydraulic-planetary cone ring parallel compound transmission mode is as follows:
first clutch C 1 52. Third clutch C 3 57. Fourth clutch C 4 13. Fifth clutch C 5 22. Sixth clutch C 6 31 and a ninth clutch C 9 310 are engaged while the second clutch C is engaged 2 56. Seventh clutch C 7 32. Eighth clutch C 8 39. Tenth clutch C 10 44 and a brake B25 are separated, the front planetary gear assembly 2 is fixedly connected into a whole, and the power is divided at the input shaft 11: one path of power is transmitted to a hydraulic transmission input shaft 51 through a first gear pair 12 to drive a variable pump 53 to work, the variable pump 53 outputs high-pressure oil to drive a fixed-displacement motor 54 to rotate, the power output by the output end of the fixed-displacement motor 54 is transmitted to a rear planet gear carrier 43 through a hydraulic transmission output shaft 55 and a fifth gear pair 311, the other path of power is transmitted to a planet cone ring type continuously variable transmission input shaft 34 through a front planet gear assembly 2 to drive a planet cone ring type continuously variable transmission 35 to work, the power output by the planet cone ring type continuously variable transmission 35 is transmitted to a rear planet gear sun gear 42 through a planet cone ring type continuously variable transmission output shaft 36, and the power transmitted to the rear planet gear carrier 43 and the power transmitted to the rear planet gear sun gear 42 are transmitted to an output shaft 6 to be output after being converged at a rear planet gear ring 41.
The method for calculating the rotating speed of the output shaft 6 in the hydraulic-planetary cone ring parallel composite transmission mode comprises the following steps:
Figure BDA0003658277480000142
in the formula, n o For the rotational speed of the output shaft 6, n I Is the rotational speed, k, of the input shaft 11 2 Of the rear planetary gear assembly 4Characteristic parameter of the planetary gear, i k Is the transmission ratio, i, of the planetary cone-ring continuously variable transmission assembly 3 1 Is the gear ratio of the first gear pair 12, i 5 The gear ratio of the fifth gear pair 311.
As shown in fig. 9, the control method of the hydraulic-planetary cone ring series compound transmission mode is as follows:
first clutch C 1 52. Second clutch C 2 56. Fifth clutch C 5 22. Sixth clutch C 6 31. Ninth clutch C 9 310 and tenth clutch C 10 44 are engaged while the third clutch C is engaged 3 57. Fourth clutch C 4 13. Seventh clutch C 7 32. Eighth clutch C 8 39 and a brake B25 are separated, power is transmitted to the hydraulic transmission input shaft 51 from the input shaft 11 through the first gear pair 12 to drive the variable pump 53 to work, the variable displacement pump 53 outputs high-pressure oil to drive the fixed displacement motor 54 to rotate, the power output by the output end of the fixed displacement motor 54 is transmitted to the front planetary gear sun gear 24 through the hydraulic transmission output shaft 55 and the second gear pair 26, the front planetary gear assembly 2 is fixedly connected into a whole, power is transmitted to the input shaft 34 of the planet cone ring type continuously variable transmission through the front planetary gear assembly 2 to drive the planet cone ring type continuously variable transmission 35 to work, the power output from the planetary cone ring type continuously variable transmission 35 is transmitted to the rear planetary gear sun gear 42 through the planetary cone ring type continuously variable transmission output shaft 36, the rear planetary gear assembly 4 is fixedly connected into a whole, and power is transmitted to the output shaft 6 through the rear planetary gear assembly 4 to be output.
The method for calculating the rotating speed of the output shaft 6 in the hydraulic-planetary cone ring series composite transmission mode comprises the following steps:
Figure BDA0003658277480000151
in the formula, n o For the rotational speed of the output shaft 6, n I For the speed of rotation of the input shaft 11, e is the displacement ratio of the hydraulic transmission assembly 5, i k Is the transmission ratio, i, of the planetary cone-ring continuously variable transmission assembly 3 1 Is the gear ratio of the first gear pair 12, i 2 Is a second gear pair 26.
As shown in fig. 10, the control method of the mechanical-hydraulic-planetary cone ring compound transmission mode is as follows:
first clutch C 1 52. Second clutch C 2 56. Fourth clutch C 4 13. Sixth clutch C 6 31. Ninth clutch C 9 310 and tenth clutch C 10 44 are engaged while the third clutch C is engaged 3 57. Fifth clutch C 5 22. Seventh clutch C 7 32. Eighth clutch C 8 39 and brake B25 are disengaged and power is split at the input shaft 11: one path of power is transmitted to the front planetary gear ring gear 21, the other path of power is transmitted to the hydraulic transmission input shaft 51 through the first gear pair 12 to drive the variable pump 53 to work, the variable displacement pump 53 outputs high-pressure oil to drive the fixed displacement motor 54 to rotate, the power output by the output end of the fixed displacement motor 54 is transmitted to the front planetary gear sun gear 24 through the hydraulic transmission output shaft 55 and the second gear pair 26, the power transmitted to the front planetary gear rim 21 and the power transmitted to the front planetary gear sun gear 24 are converged at the front planetary gear carrier 23 and then drive the planetary cone ring type continuously variable transmission 35 to work through the planetary cone ring type continuously variable transmission input shaft 34, the power output from the planetary cone ring type continuously variable transmission 35 is transmitted to the rear planetary gear sun gear 42 through the planetary cone ring type continuously variable transmission output shaft 36, the rear planetary gear assembly 4 is fixedly connected into a whole, and power is transmitted to the output shaft 6 through the rear planetary gear assembly 4 to be output.
The method for calculating the rotating speed of the output shaft 6 in the mechanical-hydraulic-planetary cone ring compound transmission mode comprises the following steps:
Figure BDA0003658277480000152
in the formula, n o For the rotational speed of the output shaft 6, n I For the speed of rotation of the input shaft 11, e is the displacement ratio of the hydraulic transmission assembly 5, k 1 Is a characteristic parameter of the planet gears of the front planetary gear assembly 2, i k Is the transmission ratio, i, of the planetary cone-ring continuously variable transmission assembly 3 1 Is the gear ratio of the first gear pair 12, i 2 Is a secondThe gear ratio of gear pair 26.
Stepless speed change switching among various transmission modes is realized by adjusting the transmission ratio of the planetary cone-ring type continuously variable transmission assembly 3, adjusting the displacement ratio of the hydraulic transmission assembly 5 and controlling the engagement between the clutch and the brake B25.
The transmission modes related to the stepless speed regulation switching among the multiple transmission modes are as follows:
"Hydraulic Transmission H1 Transmission mode" - "Hydraulic Transmission H2 Transmission mode" - "mechanical Transmission mode" - "Planet Cone Ring type continuously variable Transmission mode" -;
the transmission mode comprises a mechanical-hydraulic compound transmission mode, a mechanical-planetary cone ring compound transmission mode, a hydraulic-planetary cone ring parallel compound transmission mode, a hydraulic-planetary cone ring series compound transmission mode and a mechanical-hydraulic-planetary cone ring compound transmission mode.
For example, the following steps are carried out:
the main parameters are as follows: i.e. i 1 ＝2，i 2 ＝0.5，i 3 i 4 ＝0.5，i 5 ＝0.5，k 1 ＝1.5，k 2 ＝2.5，i k ∈[0.8，2.4]。
The output-input relation of the hydraulic transmission H1 transmission mode is as follows:
Figure BDA0003658277480000161
the output-input relation of the hydraulic transmission H2 transmission mode is as follows:
Figure BDA0003658277480000162
the output-input relation of the mechanical transmission mode is as follows:
Figure BDA0003658277480000163
the output and input relational expression of the planetary cone ring type stepless speed change transmission mode is as follows:
Figure BDA0003658277480000164
the mechanical-hydraulic compound transmission mode has the output-input relation as follows:
Figure BDA0003658277480000165
the output-input relation of the mechanical-planet conical ring compound transmission mode is as follows:
Figure BDA0003658277480000166
the output and input relation of the hydraulic-planet conical ring parallel composite transmission mode is as follows:
Figure BDA0003658277480000167
the output and input relation of the hydraulic-planet conical ring series composite transmission mode is as follows:
Figure BDA0003658277480000171
the mechanical-hydraulic-planet cone ring compound transmission mode has the output and input relational expression as follows:
Figure BDA0003658277480000172
as shown in FIG. 11, four single-flow transmission modes, i.e., a hydraulic transmission H1 transmission mode, a hydraulic transmission H2 transmission mode, a mechanical transmission mode and a planetary cone-ring continuously variable transmission mode are provided by adjusting the displacement ratio of the hydraulic transmission assembly 5, adjusting the transmission ratio of the planetary cone-ring continuously variable transmission assembly 3 and selectively controlling the engagement of the clutches and the brakesThe method. When the hydraulic transmission H1 transmission mode is adopted for starting, the output rotating speed linearly increases along with the increase of the displacement ratio e of the hydraulic transmission assembly 5, and when the e is equal to-1, the rotating speed of the output shaft of the hydraulic transmission H1 transmission mode reaches the negative maximum value-n I (ii) a When e is equal to 1, the output shaft speed of the hydraulic transmission H1 transmission mode reaches the positive maximum value n I (ii) a When e is equal to 1, the planetary cone-ring type continuously variable transmission mode can be synchronously switched to, and when the transmission ratio of the planetary cone-ring type continuously variable transmission assembly 3 is changed from 0.8 to 2.4, the output shaft speed n of the planetary cone-ring type continuously variable transmission mode is changed O Decreases non-linearly. Starting in a hydraulic transmission H2 transmission mode, linearly increasing the rotation speed of an output shaft along with the increase of the displacement ratio e of the hydraulic transmission mechanism, and when the e is equal to-1, enabling the rotation speed of the output shaft in the hydraulic transmission H2 transmission mode to reach the negative maximum value-2 n I When e is equal to 1, the output shaft speed of the hydraulic transmission H2 transmission mode reaches the positive maximum value 2n I (ii) a When the e-0.6 is satisfied, the output shaft speed of the hydraulic transmission H2 transmission mode reaches 1.2n I At this time, the mechanical transmission mode can be synchronously switched to the mechanical transmission mode, and the mechanical transmission mode has a fixed transmission ratio of 1.2n I And (5) transmission.
As shown in fig. 12, five compound transmission modes, i.e., a mechanical-hydraulic compound transmission mode, a mechanical-planetary cone ring compound transmission mode, a hydraulic-planetary cone ring parallel compound transmission mode, a hydraulic-planetary cone ring series compound transmission mode, a mechanical-hydraulic-planetary cone ring compound transmission mode, and the like, are provided by adjusting the displacement ratio of the hydraulic transmission assembly 5, adjusting the transmission ratio of the planetary cone ring type continuously variable transmission assembly 3, and selectively controlling the engagement of the clutch and the brake. The output speed of the mechanical-hydraulic compound transmission mode linearly increases along with the increase of the displacement ratio e of the hydraulic transmission assembly 5, and when the e is equal to 1, the output speed of the mechanical-hydraulic compound transmission mode reaches the maximum value of 0.67n I At the moment, the mechanical-hydraulic compound transmission mode can be synchronously switched to the hydraulic-planetary cone ring series compound transmission mode, and can also be synchronously switched to the mechanical-hydraulic-planetary cone ring compound transmission mode. When i is in the mechanical-hydraulic-planetary cone ring compound transmission mode K Mechanical-hydraulic-planetary cone ring compound transmission mode when changing from 0.8 to 2.4Rotational speed n of the output shaft O Non-linearly from 1.25n I Reduced to 0.42n I . In the hydraulic-planetary cone ring parallel compound transmission mode, when e is equal to 1 and i is satisfied K ∈[0.8，2.4]At an output shaft speed n O Increases nonlinearly with the increase of the transmission ratio of the planetary cone-ring type continuously variable transmission assembly 3 when i K When the speed is 0.8, the output shaft speed n of the hydraulic-planet conical ring parallel composite transmission mode O Having a forward minimum value of 0.9n I When i is K When the speed is 2.4, the output shaft speed n of the hydraulic-planet conical ring parallel composite transmission mode O With a positive maximum of 1.23n I Wherein, when e is 1, i K When the speed is 1, the output shaft speed of the hydraulic-planet conical ring parallel composite transmission mode reaches 1n I And at the moment, the hydraulic-planetary cone ring series composite transmission mode or the mechanical-hydraulic-planetary cone ring composite transmission mode can be synchronously switched. In the mechanical-planetary cone ring compound transmission mode, the output shaft speed n O Increases nonlinearly with the increase of the transmission ratio of the planetary cone-ring type continuously variable transmission assembly 3 when i K When equal to 0.8, the output shaft speed n of the mechanical-planet cone ring compound transmission mode O Has a minimum value of 2.3 when i K Output shaft speed n of mechanical-planetary cone ring compound transmission mode when equal to 2.4 O Has a maximum value of 2.6n I 。
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other. The device disclosed by the embodiment corresponds to the method disclosed by the embodiment, so that the description is simple, and the relevant points can be referred to the method part for description.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims (9)

1. The utility model provides a mechanical hydraulic pressure planet cone ring compound transmission which characterized in that includes:
an input assembly (1) comprising an input shaft (11), a first gear pair (12), a fourth clutch C 4 (13)；
A front planetary gear assembly (2) comprising a front planetary gear ring gear (21) and a fifth clutch C 5 (22) The front planetary gear carrier (23), the front planetary gear sun gear (24), the brake B (25), the second gear pair (26) and the front planetary gear output shaft (27), wherein the input shaft (11) passes through a fourth clutch C 4 (13) Is connected with a front planetary gear ring (21), and the front planetary gear ring (21) passes through a fifth clutch C 5 (22) Is connected with a front planetary gear carrier (23), the front planetary gear carrier (23) is connected with a front planetary gear output shaft (27), and the brake B (25) can lock the front planetary gear sun gear (24);
a planetary cone ring type continuously variable transmission assembly (3) and a sixth clutch C 6 (31) Seventh clutch C 7 (32) The planetary cone ring type continuously variable transmission comprises a third gear pair (33), a planetary cone ring type continuously variable transmission input shaft (34), a planetary cone ring type continuously variable transmission (35), a planetary cone ring type continuously variable transmission output shaft (36), an intermediate transmission shaft (37), a fourth gear pair (38) and an eighth clutch C 8 (39) Ninth clutch C 9 (310) The third gear pair (33) is connected with the fourth gear pair (38) through an intermediate transmission shaft (37), an output gear of the fourth gear pair (38) is sleeved on an output shaft (36) of the planetary cone ring type continuously variable transmission through an output gear shaft, and an input shaft (34) of the planetary cone ring type continuously variable transmission is connected with a sixth clutch C 6 (31) Is connected with the front planetary gear output shaft (27), and the third gear pair (33) passes through a seventh clutch C 7 (32) The planetary cone ring type continuously variable transmission input shaft (34) is connected with a planetary cone ring type continuously variable transmission output shaft (36) through a planetary cone ring type continuously variable transmission (35);
a rear planetary gear assembly (4) comprising a rear planetary gear ring gear (41), a rear planetary gear sun gear (42), a rear planetary gear planet carrier (43), a tenth clutch C 10 (44) The star gear ring gear (41) passes through a tenth clutch C 10 (44) Is connected with a rear planet gear carrier (43), the rear planet gear carrier (43) passes through an eighth clutch C 8 (39) Is connected with a fourth gear pair (38), and the rear planet gear sun gear (42) passes through a ninth clutch C 9 (310) Is connected with an output shaft (36) of the planetary cone ring type continuously variable transmission;
a hydraulic transmission assembly (5) comprising a hydraulic transmission input shaft (51), a first clutch C 1 (52) A variable pump (53), a fixed-displacement motor (54), a hydraulic transmission output shaft (55) and a second clutch C 2 (56) A third clutch C 3 (57) The input shaft (11) passes through a first gear pair (12) and a first clutch C 1 (52) Is connected with hydraulic transmission input shaft (51), hydraulic transmission input shaft (51) is connected with variable pump (53), variable pump (53) drive ration motor (54) work, ration motor (54) output is connected with hydraulic transmission output shaft (55), hydraulic transmission output shaft (55) are through second clutch C 2 (56) The second gear pair (26) is connected with the front planetary gear sun gear (24), and the hydraulic transmission output shaft (55) is connected with the front planetary gear sun gear (24) through a third clutch C 3 (57) The fifth gear pair (311) is connected with the rear planet gear carrier (43);
and the output shaft (6), and the output shaft (6) is connected with a rear planetary gear ring gear (41).
2. The control method of a mechano-hydraulic planetary cone-ring compound transmission as defined in claim 1, characterized in that: the switching of a single-flow transmission mode and a compound transmission mode is realized by adjusting the transmission ratio of the planetary cone ring type continuously variable transmission assembly (3), adjusting the displacement ratio of the hydraulic transmission assembly (5) and controlling the engagement switching between the clutch and the brake B (25); the single-flow transmission mode comprises a mechanical transmission mode, a hydraulic transmission mode and a planetary cone ring type stepless speed change transmission mode; the compound transmission modes comprise a mechanical-hydraulic compound transmission mode, a mechanical-planetary cone ring compound transmission mode, a hydraulic-planetary cone ring compound transmission mode and a mechanical-hydraulic-planetary cone ring compound transmission mode.
3. The control method of a mechano-hydraulic planetary cone-ring compound transmission as defined in claim 2, characterized in that: the hydraulic-planetary cone ring compound transmission mode comprises a hydraulic-planetary cone ring parallel compound transmission mode and a hydraulic-planetary cone ring series compound transmission mode.
4. The control method of a mechano-hydraulic planetary cone-ring compound transmission as defined in claim 2, characterized in that: the control method of the single flow transmission mode comprises the following steps:
the hydraulic transmission modes are divided into a hydraulic transmission H1 transmission mode and a hydraulic transmission H2 transmission mode,
hydraulic transmission H1 transmission mode: first clutch C 1 (52) And a third clutch C 3 (57) And a tenth clutch C 10 (44) Engaging while the second clutch C 2 (56) And a fourth clutch C 4 (13) Fifth clutch C 5 (22) Sixth clutch C 6 (31) Seventh clutch C 7 (32) Eighth clutch C 8 (39) Ninth clutch C 9 (310) The power is transmitted to a hydraulic transmission input shaft (51) from an input shaft (11) through a first gear pair (12) to drive a variable pump (53) to work, the variable pump (53) outputs high-pressure oil to drive a quantitative motor (54) to rotate, the power output by the output end of the quantitative motor (54) is transmitted to a rear planetary gear carrier (43) through a hydraulic transmission output shaft (55) and a fifth gear pair (311), the rear planetary gear assembly (4) is fixedly connected into a whole, and the power is transmitted to an output shaft (6) through the rear planetary gear assembly (4) to be output;
hydraulic transmission H2 transmission mode: first clutch C 1 (52) A second clutch C 2 (56) Fifth clutch C 5 (22) Seventh clutch C 7 (32) Eighth clutch C 8 (39) And a tenth clutch C 10 (44) Engaging while the third clutch C 3 (57) And a fourth clutch C 4 (13) Sixth clutch C 6 (31) Ninth clutch C 9 (310) The brake B (25) is separated, power is transmitted from the input shaft (11) to the hydraulic transmission input shaft (51) through the first gear pair (12) to drive the variable pump (53) to work, the variable pump (53) outputs high-pressure oil to drive the quantitative motor (54) to rotate, the power output by the output end of the quantitative motor (54) is transmitted to the front planetary gear sun gear (24) through the hydraulic transmission output shaft (55) and the second gear pair (26), the front planetary gear assembly (2) and the rear planetary gear assembly (4) are respectively and fixedly connected into a whole, the power is transmitted to the rear planetary gear planet carrier (43) through the third gear pair (33), the middle transmission shaft (37) and the fourth gear pair (38), and the power is transmitted to the output shaft (6) through the rear planetary gear assembly (4) to be output;
mechanical transmission mode: fourth clutch C 4 (13) Seventh clutch C 7 (32) Eighth clutch C 8 (39) Tenth clutch C 10 (44) And brake B (25) while the first clutch C is engaged 1 (52) A second clutch C 2 (56) A third clutch C 3 (57) Fifth clutch C 5 (22) Sixth clutch C 6 (31) And a ninth clutch C 9 (310) Separated, the power passes through a fourth clutch C from an input shaft (11) 4 (13) The front planetary gear ring gear (21) is driven to work, and the power output by the front planetary gear ring gear (21) passes through a front planetary gear planet carrier (23), a front planetary gear output shaft (27) and a seventh clutch C 7 (32) A third gear pair (33), an intermediate transmission shaft (37), a fourth gear pair (38) and an eighth clutch C 8 (39) The power is transmitted to a rear planetary gear carrier (43), the rear planetary gear assembly (4) is fixedly connected into a whole, and the power is transmitted to an output shaft (6) through the rear planetary gear assembly (4) to be output;
planetary cone ring type stepless speed change transmission mode: fourth clutch C 4 (13) Fifth clutch C 5 (22) Sixth clutch C 6 (31) Ninth clutch C 9 (310) And a tenth clutch C 10 (44) Engaging while the first clutch C is engaged 1 (52) A second clutch C 2 (56) A third clutch C 3 (57) Seventh clutch C 7 (32) Eighth clutch C 8 (39) Separate from brake B (25)The power is transmitted to a front planetary gear ring gear (21) by an input shaft (11), the front planetary gear assembly (2) is fixedly connected into a whole, the power is transmitted to a planetary cone ring type continuously variable transmission input shaft (34) through the front planetary gear assembly (2) to drive a planetary cone ring type continuously variable transmission (35) to work, the power output by the planetary cone ring type continuously variable transmission (35) is transmitted to a rear planetary gear sun gear (42) through a planetary cone ring type continuously variable transmission output shaft (36), the rear planetary gear assembly (4) is fixedly connected into a whole, and the power is transmitted to an output shaft (6) through the rear planetary gear assembly (4) to be output.
5. The control method of a mechano-hydraulic planetary cone-ring compound transmission as defined in claim 2, characterized in that: the control method of the compound transmission mode comprises the following steps:
mechanical-hydraulic compound transmission mode: first clutch C 1 (52) A second clutch C 2 (56) And a fourth clutch C 4 (13) Seventh clutch C 7 (32) Eighth clutch C 8 (39) And a tenth clutch C 10 (44) Engaging while the third clutch C 3 (57) Fifth clutch C 5 (22) Sixth clutch C 6 (31) Ninth clutch C 9 (310) And a brake B (25), power split at the input shaft (11): power transmission is to preceding planetary gear ring gear (21) all the way, and another way power transmits to hydraulic pressure transmission input shaft (51) through first gear pair (12) and drives variable pump (53) work, variable pump (53) output high pressure fluid drive ration motor (54) are rotatory, the power of ration motor (54) output passes through hydraulic transmission output shaft (55), second gear pair (26) transmission to preceding planetary gear sun gear (24), and the power of transmission to preceding planetary gear ring gear (21) and the power of transmission to preceding planetary gear sun gear (24) transmit to back planetary gear planet carrier (43) through preceding planetary gear output shaft (27), third gear pair (33), intermediate drive shaft (37), fourth gear pair (38) after planet carrier (23) department joins before, back planetary gear assembly (4) link firmly as an organic whole, the power is transmitted to the output shaft (6) through the rear planetary gear assembly (4) and is output;
mechanical-planetary cone ring composite transmissionMode (2): fourth clutch C 4 (13) Fifth clutch C 5 (22) Sixth clutch C 6 (31) Seventh clutch C 7 (32) Eighth clutch C 8 (39) And a ninth clutch C 9 (310) Engaging while the first clutch C is engaged 1 (52) A second clutch C 2 (56) A third clutch C 3 (57) Tenth clutch C 10 (44) And the brake B (25) is separated, the front planetary gear assembly (2) is fixedly connected into a whole, and power is transmitted to the front planetary gear assembly (2) through the input shaft (11) to be split: one path of power is transmitted to a rear planet gear carrier (43) through a front planet gear output shaft (27), a third gear pair (33), an intermediate transmission shaft (37) and a fourth gear pair (38), the other path of power drives a planet cone ring type continuously variable transmission (35) to work through a planet cone ring type continuously variable transmission input shaft (34), the power output by the planet cone ring type continuously variable transmission (35) is transmitted to a rear planet gear sun gear (42) through a planet cone ring type continuously variable transmission output shaft (36), and the power transmitted to the rear planet gear carrier (43) and the power transmitted to the rear planet gear sun gear (42) are converged at a rear planet gear ring gear (41) and then transmitted to an output shaft (6) for output;
the hydraulic-planetary cone ring compound transmission mode is divided into a hydraulic-planetary cone ring parallel compound transmission mode and a hydraulic-planetary cone ring series compound transmission mode,
the hydraulic-planet conical ring parallel composite transmission mode is as follows: first clutch C 1 (52) A third clutch C 3 (57) And a fourth clutch C 4 (13) Fifth clutch C 5 (22) Sixth clutch C 6 (31) And a ninth clutch C 9 (310) Engaging while the second clutch C 2 (56) Seventh clutch C 7 (32) Eighth clutch C 8 (39) Tenth clutch C 10 (44) And the brake B (25) is separated, the front planetary gear assembly (2) is fixedly connected into a whole, and power is divided at the input shaft (11): one path of power is transmitted to a hydraulic transmission input shaft (51) through a first gear pair (12) to drive a variable pump (53) to work, the variable pump (53) outputs high-pressure oil to drive a fixed-displacement motor (54) to rotate, and the power output by the output end of the fixed-displacement motor (54) passes through a hydraulic transmission output shaft (55) and a first gear pairThe five gear pairs (311) are transmitted to the rear planet gear carrier (43), the other path of power is transmitted to the input shaft (34) of the planetary cone ring type continuously variable transmission through the front planet gear assembly (2) to drive the planetary cone ring type continuously variable transmission (35) to work, the power output by the planetary cone ring type continuously variable transmission (35) is transmitted to the rear planet gear sun gear (42) through the output shaft (36) of the planetary cone ring type continuously variable transmission, and the power transmitted to the rear planet gear carrier (43) and the power transmitted to the rear planet gear sun gear (42) are converged at the rear planet gear ring gear (41) and then transmitted to the output shaft (6) to be output;
the hydraulic-planet conical ring series composite transmission mode is as follows: first clutch C 1 (52) A second clutch C 2 (56) Fifth clutch C 5 (22) Sixth clutch C 6 (31) Ninth clutch C 9 (310) And a tenth clutch C 10 (44) Engaging while the third clutch C 3 (57) And a fourth clutch C 4 (13) Seventh clutch C 7 (32) Eighth clutch C 8 (39) The power is transmitted from the input shaft (11) to the hydraulic transmission input shaft (51) through the first gear pair (12) to drive the variable pump (53) to work, the variable pump (53) outputs high-pressure oil to drive the quantitative motor (54) to rotate, the power output by the output end of the quantitative motor (54) is transmitted to the front planetary gear sun gear (24) through the hydraulic transmission output shaft (55) and the second gear pair (26), the front planetary gear assembly (2) is fixedly connected into a whole, the power is transmitted to the planet cone ring type stepless transmission input shaft (34) through the front planetary gear assembly (2) to drive the planet cone ring type stepless transmission (35) to work, and the power output by the planet cone ring type stepless transmission (35) is transmitted to the rear planet gear sun gear (42) through the planet cone ring type stepless transmission output shaft (36), the rear planetary gear assembly (4) is fixedly connected into a whole, and power is transmitted to the output shaft (6) through the rear planetary gear assembly (4) to be output;
mechanical-hydraulic-planet cone ring compound transmission mode: first clutch C 1 (52) A second clutch C 2 (56) And a fourth clutch C 4 (13) Sixth clutch C 6 (31) Ninth clutch C 9 (310) And a tenth clutch C 10 (44) Bonding while thirdClutch C 3 (57) Fifth clutch C 5 (22) Seventh clutch C 7 (32) Eighth clutch C 8 (39) And a brake B (25), power split at the input shaft (11): one path of power is transmitted to a front planetary gear ring gear (21), the other path of power is transmitted to a hydraulic transmission input shaft (51) through a first gear pair (12) to drive a variable pump (53) to work, the variable pump (53) outputs high-pressure oil to drive a quantitative motor (54) to rotate, the power output by the output end of the quantitative motor (54) is transmitted to a front planetary gear sun gear (24) through a hydraulic transmission output shaft (55) and a second gear pair (26), the power transmitted to the front planetary gear ring gear (21) and the power transmitted to the front planetary gear sun gear (24) are converged at a front planetary gear carrier (23) and then are transmitted to a rear planetary gear sun gear (42) through a planetary cone ring type continuously variable transmission input shaft (34) to drive a planetary cone ring type continuously variable transmission (35) to work, and the power output by the planetary cone ring type continuously variable transmission (35) is transmitted to the rear planetary gear sun gear (42) through a planetary cone ring type continuously variable transmission output shaft (36), the rear planetary gear assembly (4) is fixedly connected into a whole, and power is transmitted to the output shaft (6) through the rear planetary gear assembly (4) to be output.
6. A method of controlling a mechano-hydraulic planetary cone-ring compound transmission as claimed in claim 4, characterized in that the output shaft (6) speed n of the single flow transmission mode is o The calculation method is as follows:
the hydraulic transmission modes are divided into a hydraulic transmission H1 transmission mode and a hydraulic transmission H2 transmission mode,
hydraulic transmission H1 transmission mode:
Figure FDA0003658277470000051
in the formula, n o Is the rotational speed of the output shaft (6), n I Is the rotational speed of the input shaft (11), e is the displacement ratio of the hydraulic transmission assembly (5), i 1 Is the gear ratio of the first gear pair (12), i 5 Is the gear ratio of the fifth gear pair (311);
hydraulic transmission H2 transmission mode:
Figure FDA0003658277470000052
in the formula, n o Is the rotational speed of the output shaft (6), n I Is the rotational speed of the input shaft (11), e is the displacement ratio of the hydraulic transmission assembly (5), i 1 Is the gear ratio of the first gear pair (12), i 2 Is the gear ratio of the second gear pair (26), i 3 Is the gear ratio of the third gear pair (33), i 4 Is the gear ratio of the fourth gear pair (38);
mechanical transmission mode:
Figure FDA0003658277470000053
in the formula, n o Is the rotational speed of the output shaft (6), n I Is the rotational speed, k, of the input shaft (11) 1 Is a characteristic parameter of the planet gear of the front planet gear assembly (2), i 3 Is the gear ratio of the third gear pair (33), i 4 Is the gear ratio of the fourth gear pair (38);
planetary cone ring type stepless speed change transmission mode:
Figure FDA0003658277470000061
in the formula, n o Is the rotational speed of the output shaft (6), n I Is the rotational speed, i, of the input shaft (11) k Is the transmission ratio of the planetary cone ring type continuously variable transmission component (3).
7. A control method of a mechano-hydraulic planetary cone ring compound transmission according to claim 5, characterized in that the output shaft (6) speed n of the compound transmission mode is o The calculation method is as follows:
mechanical-hydraulic compound transmission mode:
Figure FDA0003658277470000062
in the formula, n o Is the rotational speed of the output shaft (6), n I Is the rotational speed of the input shaft (11), e is the displacement ratio of the hydraulic transmission assembly (5), k 1 Is a characteristic parameter of the planet gear of the front planet gear assembly (2), i 1 Is the gear ratio of the first gear pair (12), i 2 Is the gear ratio of the second gear pair (26), i 3 Is the gear ratio of the third gear pair (33), i 4 Is the gear ratio of the fourth gear pair (38);
mechanical-planetary cone ring compound transmission mode:
Figure FDA0003658277470000063
in the formula, n o Is the rotational speed of the output shaft (6), n I Is the rotational speed, k, of the input shaft (11) 2 Is a characteristic parameter of the planet gear of the rear planetary gear assembly (4), i k Is the transmission ratio of a planetary cone ring type continuously variable transmission assembly (3), i 2 Is the gear ratio of the second gear pair (26), i 3 Is the gear ratio of the third gear pair (33), i 4 Is the gear ratio of the fourth gear pair (38);
the hydraulic-planetary cone ring compound transmission mode is divided into a hydraulic-planetary cone ring parallel compound transmission mode and a hydraulic-planetary cone ring series compound transmission mode,
the hydraulic-planet conical ring parallel composite transmission mode is as follows:
Figure FDA0003658277470000064
in the formula, n o Is the rotational speed of the output shaft (6), n I Is the rotational speed, k, of the input shaft (11) 2 A characteristic parameter of the planet gear of the rear planetary gear assembly (4), i k Is the transmission ratio of a planetary cone ring type continuously variable transmission assembly (3), i 1 Is the gear ratio of the first gear pair (12), i 5 Is the gear ratio of the fifth gear pair (311);
the hydraulic-planet conical ring series composite transmission mode is as follows:
Figure FDA0003658277470000071
in the formula, n o Is the rotational speed of the output shaft (6), n I Is the rotational speed of the input shaft (11), e is the displacement ratio of the hydraulic transmission assembly (5), i k Is the transmission ratio of a planetary cone ring type continuously variable transmission assembly (3), i 1 Is the gear ratio of the first gear pair (12), i 2 Is the gear ratio of the second gear pair (26);
mechanical-hydraulic-planet cone ring compound transmission mode:
Figure FDA0003658277470000072
in the formula, n o Is the rotational speed of the output shaft (6), n I Is the rotational speed of the input shaft (11), e is the displacement ratio of the hydraulic transmission assembly (5), k 1 Is a characteristic parameter of the planet gear of the front planet gear assembly (2), i k Is the transmission ratio of a planetary cone ring type continuously variable transmission assembly (3), i 1 Is the gear ratio of the first gear pair (12), i 2 Is the gear ratio of the second gear pair (26).
8. A control method of an electro-mechanical-hydraulic compound transmission according to claim 2, characterized in that the stepless speed change between the plurality of transmission modes is realized by adjusting the transmission ratio of the planetary cone-ring type continuously variable transmission assembly (3), adjusting the displacement ratio of the hydraulic transmission assembly (5), controlling the engagement between the clutch and the brake B (25).
9. A method of controlling an electro-mechanical-hydraulic compound transmission as claimed in claim 8, wherein the continuously variable speed change between the plurality of transmission modes involves the following transmission modes:
"hydraulic transmission H1 transmission mode" - "hydraulic transmission H2 transmission mode" - "mechanical transmission mode" - "planetary cone-ring type continuously variable transmission mode";
a "mechanical-hydraulic compound transmission mode" - "a mechanical-planetary cone ring compound transmission mode" - "a hydraulic-planetary cone ring parallel compound transmission mode" - "a hydraulic-planetary cone ring series compound transmission mode" - "a mechanical-hydraulic-planetary cone ring compound transmission mode".
CN202210568748.6A 2022-05-24 2022-05-24 Mechanical hydraulic planetary cone ring composite transmission device and control method thereof Pending CN114877040A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202210568748.6A CN114877040A (en) 2022-05-24 2022-05-24 Mechanical hydraulic planetary cone ring composite transmission device and control method thereof

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202210568748.6A CN114877040A (en) 2022-05-24 2022-05-24 Mechanical hydraulic planetary cone ring composite transmission device and control method thereof

Publications (1)

Publication Number Publication Date
CN114877040A true CN114877040A (en) 2022-08-09

Family

ID=82678373

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202210568748.6A Pending CN114877040A (en) 2022-05-24 2022-05-24 Mechanical hydraulic planetary cone ring composite transmission device and control method thereof

Country Status (1)

Country Link
CN (1) CN114877040A (en)

Similar Documents

Publication Publication Date Title
CN205298454U (en) Hydraulic pressure machinery infinitely variable transmission for loader
CN111207198B (en) Multi-mode mechanical-hydraulic composite transmission device integrating gear, hydraulic pressure and metal belt
CN102943859B (en) Hydraulic mechanical continuously variable transmission for loader
US4008628A (en) Hydromechanical transmission
CN110056634A (en) Three four sections of planet row hydraulic machinery infinitely variable transmissions
WO2022266988A1 (en) Multi-mode composite transmission device that integrates gear-hydraulic pressure-pyramid
CN107191568B (en) Mechanical-hydraulic mixed drive gearbox
CN104179925A (en) Convergence type hydraulic and mechanical continuously variable transmission provided with double planet rows
CN104088978A (en) Single-planet-row convergence hydraulic mechanical continuously variable transmission
CN109723788A (en) A kind of variable speed drive
US4976665A (en) Vehicle drive device with a hydrostatic-mechanical power splitting transmission
CN112377593A (en) Double-stage planetary gear return flow type hydraulic mechanical stepless transmission system
CN101793315B (en) Mechanical and hydraulic combined power transmission mechanism
RU2719741C1 (en) Hydromechanical transmission
CN207111873U (en) Hydraulic machinery stepless speed change device mechanical gear box
CN209324954U (en) A kind of tractor infinitely variable transmission of twin shaft confluence output
US4134311A (en) Hydromechanical transmission with two planetary assemblies that are clutchable to both the input and output shafts
CN108286590B (en) Eight-gear fixed-shaft speed change mechanism of hinged dumper, gearbox thereof and implementation method
CN114877040A (en) Mechanical hydraulic planetary cone ring composite transmission device and control method thereof
CN107166005B (en) Mechanical-hydraulic mixes stepless transfer gear box
CN114909453A (en) Electromechanical-hydraulic composite transmission device and control method thereof
CN112377592A (en) Single-stage planetary gear return flow type hydraulic mechanical stepless transmission system
WO2017004782A1 (en) Combined hydraulic transmission
CN114607746A (en) Transmission device with coexisting series and parallel hydraulic machinery and control method thereof
CN211343920U (en) Hydraulic machinery continuously variable transmission

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination