CN114877046A - Multi-mode mechanical hydraulic transmission device - Google Patents

Multi-mode mechanical hydraulic transmission device Download PDF

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Publication number
CN114877046A
CN114877046A CN202210460276.2A CN202210460276A CN114877046A CN 114877046 A CN114877046 A CN 114877046A CN 202210460276 A CN202210460276 A CN 202210460276A CN 114877046 A CN114877046 A CN 114877046A
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clutch
transmission
gear
hydraulic transmission
assembly
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CN202210460276.2A
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CN114877046B (en
Inventor
潘张成
韩清振
朱林
邓耀骥
陈栋
贺奇
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Yangzhou University
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Yangzhou University
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0078—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratio comprising twelve or more forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2061—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with twelve engaging means

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

Abstract

The invention discloses a multi-mode machine hydraulic transmission device, which comprises an input shaft, a hydraulic transmission assembly, a transmission mechanism and a transmission mechanism, wherein the input end of the hydraulic transmission assembly is connected with the input shaft; the input end of the front planet wheel is connected with the input shaft; the output end of the rear planet wheel assembly is connected with an output shaft; the output end of the hydraulic transmission component can be connected with the input end of the middle planetary wheel component; the input end of the double-annular transmission assembly is connected with the input shaft, and the double-annular transmission assembly, the forward planet wheel assembly and the hydraulic transmission assembly are connected in parallel; the invention realizes the power transmission in multiple working modes by selecting the working states of the hydraulic transmission assembly and the double annular transmission assembly, and has wider application range.

Description

Multi-mode mechanical hydraulic transmission device
Technical Field
The invention relates to the technical field of power transmission, in particular to a multi-mode mechanical hydraulic transmission device.
Background
There are various ways to realize power transmission, such as hydraulic transmission, ring transmission, gear transmission, etc., and the single hydraulic transmission has lower efficiency although the transmission power is larger; the ring transmission can realize stepless speed change, but has a limited transmission ratio range; the gear transmission is highly efficient, but it is difficult to realize stepless speed change. In the prior art, the power transmission is realized by adopting a single power transmission mode, the device cannot adapt to various complex working conditions, and the application range is narrow.
Disclosure of Invention
This section is for the purpose of summarizing some aspects of embodiments of the invention and to briefly introduce some preferred embodiments. In this section, as well as in the abstract and the title of the invention of this application, simplifications or omissions may be made to avoid obscuring the purpose of the section, the abstract and the title, and such simplifications or omissions are not intended to limit the scope of the invention.
The present invention has been made in view of the above and/or other problems occurring in the conventional power transmission.
Therefore, the invention aims to provide a multi-mode mechanical hydraulic transmission device which can realize power transmission in multiple working modes by selecting the working states of a hydraulic transmission assembly and a double annular transmission assembly and has wider application range.
In order to solve the technical problems, the invention provides the following technical scheme: a multi-mode hydraulic transmission device comprises a transmission device,
an input shaft is arranged at the front end of the motor,
the input end of the hydraulic transmission assembly is connected with the input shaft;
the input end of the front planet wheel is connected with the input shaft;
the middle planet wheel component is arranged on the upper portion of the planet wheel component,
the front planet wheel assembly, the middle planet wheel assembly and the rear planet wheel assembly are connected in series through an intermediate shaft, and the output end of the rear planet wheel assembly is connected with an output shaft;
the output end of the hydraulic transmission component can be connected with the input end of the middle planetary wheel component;
the input end of the double-annular transmission assembly is connected with the input shaft, and the double-annular transmission assembly, the forward planet wheel assembly and the hydraulic transmission assembly are connected in parallel.
As a preferable aspect of the multi-mode mechanical hydraulic transmission of the present invention, wherein: preceding planet wheel subassembly includes preceding planet carrier, preceding sun gear and the preceding ring gear of input shaft, well planet wheel subassembly includes well sun gear, the well ring gear of being connected with preceding sun gear and the well planet carrier that can be connected with preceding planet carrier, back planet wheel subassembly includes the back ring gear of being connected with well sun gear, the back planet carrier of being connected with well sun gear and the back sun gear of being connected in the jackshaft of ability, preceding planet carrier and well planet carrier are all and the intermediate shaft is connected.
As a preferable aspect of the multi-mode mechanical hydraulic transmission of the present invention, wherein: the front planetary assembly also includes a front brake for selectively securing the front sun gear.
As a preferable aspect of the multi-mode mechanical hydraulic transmission of the present invention, wherein: the mid-planetary assembly also includes a mid-brake for selectively securing the mid-sun gear.
As a preferable aspect of the multi-mode mechanical hydraulic transmission of the present invention, wherein: the hydraulic transmission subassembly includes the hydraulic transmission input shaft, be connected with the hydraulic transmission input gear pair on the hydraulic transmission input shaft, the output of hydraulic transmission input gear pair is connected with the variable pump in a controllable way, the variable pump is used for driving the ration motor, the output of ration motor is connected with the hydraulic transmission output shaft, is connected with the first output gear pair of hydraulic transmission on the hydraulic transmission output shaft, the first output gear pair ability of hydraulic transmission and preceding planet frame are connected.
As a preferable aspect of the multi-mode mechanical hydraulic transmission of the present invention, wherein: the output end of the quantitative motor is further connected with a hydraulic transmission second output gear pair, and the hydraulic transmission second output gear pair can be connected with the front sun gear.
As a preferable aspect of the multi-mode mechanical hydraulic transmission of the present invention, wherein: double annular transmission subassembly includes double annular transmission input shaft, be connected with preceding annular transmission mechanism and can be vice double annular transmission input gear pair of being connected with the hydraulic transmission gear on the double annular transmission input shaft, preceding annular transmission mechanism's output is connected with back annular transmission mechanism, back annular transmission mechanism's output is connected with double annular transmission output shaft, be connected with double annular transmission output gear pair on the double annular transmission output shaft, double annular transmission output gear pair can be connected with well sun gear.
As a preferable aspect of the multi-mode mechanical hydraulic transmission of the present invention, wherein: the hydrostatic transmission assembly also includes a first clutch for selectively connecting the input shaft for common rotation with the hydrostatic transmission input shaft, a second clutch for selectively connecting the hydrostatic transmission output shaft for common rotation with the forward carrier, and a third clutch for selectively connecting the hydrostatic transmission output shaft for common rotation with the forward sun gear.
As a preferable aspect of the multi-mode mechanical hydraulic transmission of the present invention, wherein: the dual ring transmission assembly further includes a fourth clutch for selectively connecting the dual ring transmission input shaft for common rotation with the input shaft and a fifth clutch for selectively connecting the dual ring output shaft for common rotation with the mid sun gear.
As a preferable aspect of the multi-mode mechanical hydraulic transmission of the present invention, wherein: the mid-planet assembly further includes a sixth clutch for selectively connecting the mid-sun gear to the mid-sun gear for common rotation, the rear planet assembly further includes a seventh clutch for selectively connecting the mid-sun gear to the rear ring gear for common rotation, an eighth clutch for selectively connecting the mid-sun gear to the rear planet carrier for common rotation, a ninth clutch for selectively connecting the rear ring gear to the output shaft for common rotation, and a tenth clutch for selectively connecting the rear planet carrier to the output shaft for common rotation.
The invention has the beneficial effects that: the invention adopts 4 hydraulic transmission modes, which can meet the requirements of forward and backward speed regulation; the double annular transmission mode enlarges the speed regulation range and can provide stepless speed regulation for the advancing direction of the output end; the gear mode can meet the requirements of forward and backward gears; the multi-gear not only enlarges the freedom degree of speed regulation, but also has stronger fault-tolerant function; 4 gear hydraulic transmission modes are provided, and the requirements of various speed regulation ranges and precision on high-power high-efficiency stepless speed regulation are met; the double-annular hydraulic transmission mechanism has 2 double-annular hydraulic transmission modes, and meets the high-precision stepless speed regulation requirements of various speed regulation ranges and power.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without inventive exercise. Wherein:
FIG. 1 is a schematic diagram of the structure of the present invention.
FIG. 2 is a power flow diagram for gear F (H1) according to the present invention.
FIG. 3 is a power flow diagram for gear F (H2) according to the present invention.
FIG. 4 is a power flow diagram for gear F (H3) according to the present invention.
FIG. 5 is a power flow diagram for gear F (H4) according to the present invention.
FIG. 6 is a schematic diagram of the power flow of the F (C) gear of the present invention.
Fig. 7 is a power flow diagram of the F (M1) range of the present invention.
Fig. 8 is a power flow diagram for the F (M2) range of the present invention.
FIG. 9 is a schematic diagram of the power flow for the F (HM1) range of the present invention.
FIG. 10 is a schematic diagram of the power flow for the F (HM2) range of the present invention.
FIG. 11 is a schematic diagram of the power flow for the F (HM3) range of the present invention.
FIG. 12 is a schematic diagram of the power flow for the F (HM4) range of the present invention.
Fig. 13 is a power flow diagram of the F (CH1) range of the present invention.
Fig. 14 is a power flow diagram of the F (CH2) range of the present invention.
Wherein, 100 input shaft, 200 front planet wheel assembly, 201 front sun wheel, 202 front planet carrier, 203 front ring gear, 204 front brake, 300 hydraulic transmission assembly, 301 hydraulic transmission input gear pair, 302 hydraulic transmission input shaft, 303 first clutch, 304 variable displacement pump, 305 fixed displacement motor, 306 first hydraulic transmission output gear pair, 307 second clutch, 308 third clutch, 309 hydraulic transmission output shaft, 310 second hydraulic transmission output gear pair, 400 middle planet wheel assembly, 401 middle ring gear, 402 middle planet carrier, 403 middle sun wheel, 404 middle brake, 405 sixth clutch, 500 rear planet wheel assembly, 501 rear ring gear, 502 seventh clutch, 503 ninth clutch, 504 eighth clutch, 505 tenth clutch, 506 rear planet carrier, 507 rear sun wheel, 600 middle shaft, 700 output shaft, 800 double ring transmission assembly, 801 fourth clutch, 802 double ring transmission input shaft, 803 a front ring gear, 804 a rear ring gear, 805 a double ring gear output shaft, 806 a fifth clutch, 807 a double ring gear output gear pair, 808 a double ring gear input gear pair.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, but the present invention may be practiced in other ways than those specifically described and will be readily apparent to those of ordinary skill in the art without departing from the spirit of the present invention, and therefore the present invention is not limited to the specific embodiments disclosed below.
Furthermore, reference herein to "one embodiment" or "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one implementation of the invention. The appearances of the phrase "in one embodiment" in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments.
Example 1
Referring to fig. 1 to 14, the embodiment provides a multi-mode mechanical hydraulic transmission device, which can realize power transmission in multiple working modes by selecting working states of a hydraulic transmission assembly 300, a planetary gear assembly 500 and a double annular transmission assembly 800, and has a wider application range.
A multi-mode mechanical hydraulic transmission device comprises an input shaft 100, a middle planetary wheel assembly 400, a rear planetary wheel assembly 500, a hydraulic transmission assembly 300 and a double-annular transmission assembly 800, wherein the input shaft 100 is connected with the input end of the hydraulic transmission assembly 300, the input end of a front planetary wheel assembly 200 and the input end of the double-annular transmission assembly 800, the front planetary wheel assembly 200, the middle planetary wheel assembly 400 and the rear planetary wheel assembly 500 are connected in series through an intermediate shaft 600, and the output end of the rear planetary wheel assembly 500 is connected with an output shaft 700; the output end of the hydraulic transmission assembly 300 can be connected with the input end of the middle planetary gear assembly 400; the input of the dual annulus drive assembly 800 is connected to the input shaft 100, and the dual annulus drive assembly 800, the front starwheel assembly 200 and the hydrostatic drive assembly 300 are connected in parallel.
Further, the front planetary assembly 200 includes a front brake 204, a front carrier 202, a front sun gear 201, and a front ring gear 203 connected to the input shaft 100, the front brake 204 is used for selectively fixing the front sun gear 201, the middle planetary assembly 400 includes a middle brake 404, a middle sun gear 403, a middle ring gear 401 connected to the front sun gear 201, and a middle carrier 402 connectable to the front carrier 202, the middle brake 404 is used for selectively fixing the middle sun gear 403, the rear planetary assembly 500 includes a rear ring gear 501 connectable to the middle sun gear 403, a rear carrier 506 connectable to the middle sun gear 403, and a rear sun gear 507 connected to the middle shaft 600, and the front carrier 202 and the middle carrier 402 are connected to the middle shaft 600.
Further, the hydraulic transmission assembly 300 includes a hydraulic transmission input shaft 302, a first clutch 303, a second clutch 307 and a third clutch 308, the hydraulic transmission input shaft 302 is connected with a hydraulic transmission input gear pair 301, an output end of the hydraulic transmission input gear pair 301 is controllably connected with a variable pump 304, a displacement ratio of the hydraulic transmission mechanism assembly is adjusted by adjusting a displacement of the variable pump 304, the variable pump 304 is used for driving a fixed-displacement motor 305, an output end of the fixed-displacement motor 305 is connected with a hydraulic transmission output shaft 309, the hydraulic transmission output shaft 309 is connected with a hydraulic transmission first output gear pair and a hydraulic transmission second output gear pair, the hydraulic transmission first output gear pair is connected with the front planet carrier 202, the hydraulic transmission second output gear pair is connected with the front sun gear 201, the first clutch 303 is used for selectively connecting the input shaft 100 to the hydraulic transmission input shaft 302 for common rotation, the second clutch 307 is used to selectively connect the hydrostatic transmission output shaft 309 to the front carrier 202 for common rotation, and the third clutch 308 is used to selectively connect the hydrostatic transmission output shaft 309 to the front sun gear 201 for common rotation.
Further, dual ring drive assembly 800 includes a dual ring drive input shaft 802, a fourth clutch 801, and a fifth clutch 806, a front ring drive 803 and a dual ring drive input gear set 808 connectable to a hydraulically driven gear set are coupled to dual ring drive input shaft 802, a rear ring drive 804 is coupled to an output of front ring drive 803, a dual ring drive output shaft 805 is coupled to an output of rear ring drive 804, a dual ring drive output gear set 807 is coupled to dual ring drive output shaft 805, dual ring drive output gear set 807 is connectable to sun gear 403, fourth clutch 801 is configured to selectively couple dual ring drive input shaft 802 to input shaft 100 for common rotation, and fifth clutch 806 is configured to selectively couple dual ring drive output shaft 700 to sun gear 403 for common rotation.
Further, the mid-planetary assembly 400 further includes a sixth clutch 405, the sixth clutch 405 for selectively connecting the mid-ring 401 to the mid-sun gear 403 for common rotation, the rear planetary assembly 500 further includes a seventh clutch 502, an eighth clutch 504, a ninth clutch 503 and a tenth clutch 505, the seventh clutch 502 for selectively connecting the mid-sun gear 403 to the rear ring 501 for common rotation, the eighth clutch 504 for selectively connecting the mid-sun gear 403 to the rear carrier 506 for common rotation, the ninth clutch 503 for selectively connecting the rear ring 501 to the output shaft 700 for common rotation, and the tenth clutch 505 for selectively connecting the rear carrier 506 to the output shaft 700 for common rotation.
The first clutch 303, the second clutch 307, the seventh clutch 502, the tenth clutch 505 and the mid-brake 404 are engaged to realize first hydraulic transmission between the input shaft 100 and the output shaft 700; the first clutch 303, the second clutch 307, the eighth clutch 504, the ninth clutch 503 and the mid-brake 404 are engaged to realize second hydraulic transmission between the input shaft 100 and the output shaft 700; the first clutch 303, the second clutch 307, the seventh clutch 502, the eighth clutch 504, the ninth clutch 503 and the tenth clutch 505 are engaged to realize the third hydraulic transmission between the input shaft 100 and the output shaft 700; the first clutch 303, the third clutch 308, the sixth clutch 405, the seventh clutch 502, and the ninth clutch 503 are engaged to realize the fourth hydraulic transmission between the input shaft 100 and the output shaft 700.
Double ring transmission between the input shaft 100 and the output shaft 700 is achieved by engaging the fourth clutch 801, the fifth clutch 806, the seventh clutch 502, the eighth clutch 504, the ninth clutch 503 and the tenth clutch 505.
Engaging the seventh clutch 502, the tenth clutch 505, the front brake 204 and the middle brake 404 to realize the first gear transmission between the input shaft 100 and the output shaft 700; the eighth clutch 504, the ninth clutch 503, the front brake 204 and the mid-brake 404 are engaged to realize the second gear transmission between the input shaft 100 and the output shaft 700.
The first clutch 303, the second clutch 307, the sixth clutch 405, the seventh clutch 502 and the ninth clutch 503 are engaged to realize the first gear hydraulic transmission between the input shaft 100 and the output shaft 700; the first clutch 303, the third clutch 308, the seventh clutch 502 and the ninth clutch 503 are engaged to realize the second gear hydraulic transmission between the input shaft 100 and the output shaft 700; the first clutch 303, the third clutch 308, the seventh clutch 502 and the tenth clutch 505 are engaged to realize the third gear hydraulic transmission between the input shaft 100 and the output shaft 700; the first clutch 303, the third clutch 308, the eighth clutch 504 and the ninth clutch 503 are engaged to realize the fourth gear hydraulic transmission between the input shaft 100 and the output shaft 700.
The fourth clutch 801, the fifth clutch 806, the seventh clutch 502, the tenth clutch 505 and the front brake 204 are engaged to realize a first double-ring hydraulic transmission between the input shaft 100 and the output shaft 700; a second double-ring hydraulic transmission between input shaft 100 and output shaft 700 is achieved by engaging eighth clutch 504, ninth clutch 503 and front brake 204.
The invention realizes a plurality of working modes, including 4 hydraulic transmission modes, 1 double annular transmission mode, 2 gear transmission modes, 4 gear hydraulic transmission modes and 2 double annular hydraulic transmission modes, and the speed regulation requirements of forward and backward can be met in the 4 hydraulic transmission modes; the double annular transmission mode enlarges the speed regulation range and can provide stepless speed regulation for the advancing direction of the output end; the gear transmission mode can meet the requirements of forward and backward gears; the multi-gear not only enlarges the freedom degree of speed regulation, but also has stronger fault-tolerant function; 4 gear hydraulic transmission modes meet the requirements of high-power high-efficiency stepless speed regulation in various speed regulation ranges and precision; 2 double annular hydraulic transmission modes meet the high-precision stepless speed regulation requirements of various speed regulation ranges and powers.
Example 2
Referring to fig. 2 to 14, the present embodiment provides a multi-mode hydraulic transmission, and is different from embodiment 1 in that it can calculate the rotation speed of the output shaft 700 in each transmission mode.
A multi-mode mechanical hydraulic transmission device has a hydraulic transmission mode, a double annular transmission mode, a gear hydraulic transmission mode and a double annular transmission mode, and the states of all mode switching elements and speed regulation relational expressions are shown in a table 1.
TABLE 1 relational expression of states and speed regulation of switching elements of various transmission modes
Figure BDA0003620276770000071
Figure BDA0003620276770000081
i 1 For hydraulic transmission of the input gear ratio of gear pair 301, i 2 Is the gear ratio of the first hydraulic output gear pair 306, i 3 For the gear ratio of the second hydraulic output gear pair 310, i 4 Is the gear ratio of double-ring transmission input gear pair 808, i 5 Is the transmission ratio, k, of the double-ring transmission output gear pair 807 1 For a characteristic parameter of the front planet gear, k 2 For a characteristic parameter of the central planet, k 3 For the rear planetary gear characteristic, e is the displacement ratio of the hydrostatic transmission assembly 300, n e Is the input speed, n, of the engine o Is the output rotational speed, i, of the output shaft 700 T ＝i T1 i T2 Is the transmission ratio, i, when the front endless transmission 803 and the rear endless transmission 804 are connected together in series T1 Is the gear ratio, i, of the front ring gear 803 T2 For the gear ratio of the rear ring gear 804, ". tangle-solidup" indicates the shift element engaged, ". DELTA" indicates the shift element disengaged, C 1 ～C 10 Respectively represent a first clutch to a tenth clutch, B 1 Represents a medium brake, B 2 Representing the front brakes.
Figure BDA0003620276770000091
Figure BDA0003620276770000092
Figure BDA0003620276770000093
The method comprises the following specific steps:
the 1 hydraulic transmission mode comprises an F (H1) gear, an F (H2) gear, an F (H3) gear and an F (H4) gear,
f (H1) range: as shown in fig. 2, when the first clutch 303, the second clutch 307, the seventh clutch 502, the tenth clutch 505, and the middle brake 404 are engaged, the other clutches and the brake are disengaged, the hydraulic transmission assembly 300 is in an operating state, the engine power is transmitted to the hydraulic transmission output shaft 309 through the input shaft 100, the hydraulic transmission input gear pair 301, the variable pump 304, and the fixed-displacement motor 305 in sequence, and then is output from the output shaft 700 through the first hydraulic transmission output gear pair 306, the front carrier 202, the middle shaft 600, the rear sun gear 507, and the rear carrier 506 in sequence, at this time, the relationship between the output rotational speed and the input rotational speed is,
Figure BDA0003620276770000094
f (H2) range: as shown in fig. 3, when the first clutch 303, the second clutch 307, the eighth clutch 504, the ninth clutch 503 and the middle brake 404 are engaged and the other clutches and brakes are disengaged, and the hydraulic transmission assembly 300 is in a working state, the engine power is transmitted to the hydraulic transmission output shaft 309 through the input shaft 100, the hydraulic transmission input gear pair 301, the variable pump 304 and the fixed-displacement motor 305 in sequence, and then is output from the output shaft 700 through the first hydraulic transmission output gear pair 306, the front carrier 202, the middle shaft 600, the rear sun gear 507 and the rear ring gear 501 in sequence, at this time, the relationship between the output rotation speed and the input rotation speed is,
Figure BDA0003620276770000095
f (H3) range: as shown in fig. 4, when the first clutch 303, the second clutch 307, the seventh clutch 502, the eighth clutch 504, the ninth clutch 503 and the tenth clutch 505 are engaged and the other clutches and the brake are disengaged, and the hydraulic transmission assembly 300 is in a working state, the engine power is transmitted to the first hydraulic transmission output gear pair 306 through the input shaft 100, the hydraulic transmission input gear pair 301, the variable displacement pump 304, the fixed displacement motor 305 and the hydraulic transmission output shaft 309 in sequence, and then is output from the output shaft 700 through the front carrier 202, the intermediate shaft 600 and the rear planetary gear assembly 500 fixedly connected as a whole in sequence, at this time, the relationship between the output rotating speed and the input rotating speed is,
Figure BDA0003620276770000101
f (H4) range: as shown in fig. 5, when the first clutch 303, the third clutch 308, the sixth clutch 405, the seventh clutch 502, and the ninth clutch 503 are engaged and the other clutches and brakes are disengaged, and the hydraulic transmission assembly 300 is in an operating state, the engine power is transmitted to the second hydraulic transmission output gear pair 310 through the input shaft 100, the hydraulic transmission input gear pair 301, the variable displacement pump 304, the fixed displacement motor 305, and the hydraulic transmission output shaft 309 in sequence, and then is output from the output shaft 700 through the middle ring gear 401, the middle sun gear 403, and the rear ring gear 501 in sequence, at this time, the relationship between the output rotation speed and the input rotation speed is,
Figure BDA0003620276770000102
2 double ring transmission mode, which has gear f (c), as shown in fig. 6, when the fourth clutch 801, the fifth clutch 806, the seventh clutch 502, the eighth clutch 504, the ninth clutch 503 and the tenth clutch 505 are engaged, and the other clutches and the brake are disengaged, the engine power is transmitted to the double ring transmission assembly 800 via the input shaft 100, and then is output from the output shaft 700 via the rear ring gear 501, at which time, the relationship between the output rotational speed and the input rotational speed is,
Figure BDA0003620276770000103
3-gear transmission modes including F (M1) gear and F (M2) gear;
f (M1) range: as shown in fig. 7, the seventh clutch 502, the tenth clutch 505, the front brake 204 and the middle brake 404 are engaged, the other clutches and brakes are disengaged, the engine power is transmitted to the front ring gear 203 and the front carrier 202 through the input shaft 100 in turn, and then is output from the output shaft 700 through the middle shaft 600, the rear sun gear 507 and the rear carrier 506 in turn, at this time, the relationship between the output rotational speed and the input rotational speed is,
Figure BDA0003620276770000104
f (M2) range: as shown in fig. 8, the eighth clutch 504, the ninth clutch 503, the front brake 204 and the middle brake 404 are engaged, the other clutches and brakes are disengaged, the engine power is transmitted to the front ring gear 203 and the front carrier 202 via the input shaft 100, and then is output from the output shaft 700 via the middle shaft 600, the rear sun gear 507 and the rear ring gear 501 in turn, at this time, the relationship between the output rotational speed and the input rotational speed is,
Figure BDA0003620276770000105
4-gear hydrostatic transmission modes including F (HM1), F (HM2), F (HM3) and F (HM 4);
f (HM1) range: as shown in fig. 9, the first clutch 303, the second clutch 307, the sixth clutch 405, the seventh clutch 502, and the ninth clutch 503 are engaged, and the other clutches and the brake are disengaged, the engine power is split by the input shaft 100, one path is transmitted to the front carrier 202 through the hydraulic transmission assembly 300, the other path is directly transmitted to the front ring gear 203, the converged power is output from the output shaft 700 through the front sun gear 201, the middle ring gear 401, and the rear ring gear 501, and at this time, the relationship between the output rotational speed and the input rotational speed is,
Figure BDA0003620276770000111
f (HM2) range: as shown in fig. 10, the first clutch 303, the third clutch 308, the seventh clutch 502 and the ninth clutch 503 are engaged, the other clutches and the brake are disengaged, the engine power is split by the input shaft 100, one is directly transmitted to the front ring gear 203, the other is split again at the output end of the hydraulic transmission assembly 300, one is transmitted to the front sun gear 201, after being converged with the power transmitted to the front ring gear 203, the one is transmitted to the middle planet carrier 402 through the front planet carrier 202, the other is directly transmitted to the middle ring gear 401, after being converged with the power transmitted to the middle planet carrier 402, the other is sequentially transmitted to the middle sun gear 501 and the rear ring gear 501, and then is output from the output shaft 700, at this time, the relationship between the output rotation speed and the input rotation speed is,
Figure BDA0003620276770000112
f (HM3) range: as shown in fig. 11, the first clutch 303, the third clutch 308, the seventh clutch 502 and the tenth clutch 505 are engaged, the other clutches and the brake are disengaged, the hydraulic transmission assembly 300 is in an operating state, the engine power is split by the input shaft 100, one path is directly transmitted to the front ring gear 203, the other path is split again at the output end of the hydraulic transmission assembly 300, one path is transmitted to the front sun gear 201 and the power transmitted to the front ring gear 203 after merging, is transmitted to the middle carrier 402 and the rear sun gear 507 through the front carrier 202, one path is directly transmitted to the middle ring gear 401, and is transmitted to the rear ring gear 501 through the middle sun gear 403 after merging with the power transmitted to the rear sun gear 507 and is output from the output shaft 700 after merging with the rear carrier 506, at this time, the relationship between the output rotational speed and the input rotational speed is,
Figure BDA0003620276770000113
f (HM4) range: as shown in fig. 12, the first clutch 303, the third clutch 308, the eighth clutch 504 and the ninth clutch 503 are engaged, the other clutches and the brake are disengaged, the hydraulic transmission assembly 300 is in an operating state, the engine power is split by the input shaft 100, one path is directly transmitted to the front ring gear 203, the other path is split again at the output end of the hydraulic transmission mechanism, one path is transmitted to the front sun gear 201 and the power transmitted to the front ring gear 203 are converged, then transmitted to the middle carrier 402 and the rear sun gear 507 through the front carrier 202, one path is directly transmitted to the middle ring gear 401, and the power transmitted to the middle carrier 402 is converged, then transmitted to the rear carrier 506 through the middle sun gear 403, and the power transmitted to the rear sun gear 507 is converged by the rear ring gear 501 and then output from the output shaft 700, at this time, the relationship between the output rotation speed and the input rotation speed is,
Figure BDA0003620276770000121
4-gear hydrostatic transmission mode including F (CH1) and F (CH2) gears;
f (CH1) range: as shown in fig. 13, the fourth clutch 801, the fifth clutch 806, the seventh clutch 502, the tenth clutch 505, and the front brake 204 are engaged, and the other clutches and brakes are disengaged, the double ring transmission assembly 800 is in an operating state, the engine power is split by the input shaft 100, one path is transmitted to the rear sun gear 507 via the front ring gear 203, the front carrier 202, and the intermediate shaft 600, the other path is transmitted to the rear ring gear 501 via the double ring transmission mechanism, the converged power is output from the output shaft 700 via the rear carrier 506, at this time, the relationship between the output rotational speed and the input rotational speed is,
Figure BDA0003620276770000122
f (CH2) range: as shown in fig. 14, the eighth clutch 504, the ninth clutch 503 and the front brake 204 are engaged, the other clutches and brakes are disengaged, the double ring transmission assembly 800 is in an operating state, the engine power is split by the input shaft 100, one path is transmitted to the rear sun gear 507 through the front ring gear 203, the front carrier 202 and the intermediate shaft 600, the other path is transmitted to the rear carrier 506 through the double ring transmission mechanism, the converged power is output from the output shaft 700 through the rear ring gear 501, at this time, the relationship between the output rotational speed and the input rotational speed is,
Figure BDA0003620276770000123
it should be noted that the above-mentioned embodiments are only for illustrating the technical solutions of the present invention and not for limiting, and although the present invention has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that modifications or equivalent substitutions may be made on the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, which should be covered by the claims of the present invention.

Claims (10)

1. A multi-mode machine hydraulic transmission, characterized by: which comprises the steps of preparing a mixture of a plurality of raw materials,
an input shaft (100);
the hydraulic transmission assembly (300), wherein the input end of the hydraulic transmission assembly (300) is connected with the input shaft (100);
the input end of the front planet wheel assembly (200) is connected with the input shaft (100);
a central planet assembly (400);
the front planet wheel assembly (200), the middle planet wheel assembly (400) and the rear planet wheel assembly (500) are connected in series through an intermediate shaft (600), and the output end of the rear planet wheel assembly (500) is connected with an output shaft (700);
the output end of the hydraulic transmission assembly (300) can be connected with the input end of the middle planetary wheel assembly (400);
the input end of the double-annular transmission assembly (800) is connected with the input shaft (100), and the double-annular transmission assembly (800), the front planet wheel assembly (200) and the hydraulic transmission assembly (300) are connected in parallel.
2. A multi-mode mechatronic transmission as in claim 1, wherein: preceding planet gear assembly (200) are including preceding planet carrier (202), preceding sun gear (201) and preceding ring gear (203) be connected with input shaft (100), well planet gear assembly (400) are including well sun gear (403), well ring gear (401) be connected with preceding sun gear (201) and well planet carrier (402) that can be connected with preceding planet carrier (202), back planet carrier (506) that back planet gear assembly (500) are connected including back ring gear (501) that can be connected with well sun gear (403), ability and well sun gear (403) and connect back sun gear (507) on jackshaft (600), preceding planet carrier (202) and planet carrier (402) are all connected with jackshaft (600).
3. The multi-mode mechatronic transmission of claim 2, wherein: the forward planetary assembly (200) further includes a forward brake (204), the forward brake (204) for selectively securing the forward sun gear (201).
4. The multi-mode mechatronic transmission of claim 2, wherein: the middle planetary wheel assembly (400) further comprises a middle brake (404), and the middle brake (404) is used for selectively fixing the middle sun wheel (403).
5. A multi-mode machine hydraulic transmission as claimed in any one of claims 2 to 4, wherein: the hydraulic transmission subassembly (300) includes hydraulic transmission input shaft (302), be connected with hydraulic transmission input gear pair (301) on hydraulic transmission input shaft (302), the output of hydraulic transmission input gear pair (301) is connected with variable pump (304) in a controllable way, variable pump (304) are used for driving quantitative motor (305), the output of quantitative motor (305) is connected with hydraulic transmission output shaft (309), is connected with the first output gear pair of hydraulic transmission on hydraulic transmission output shaft (309), the first output gear pair of hydraulic transmission can with preceding planet frame (202) be connected.
6. The multi-mode mechatronic transmission of claim 5, wherein: the hydraulic transmission output shaft (309) is also connected with a hydraulic transmission second output gear pair, and the hydraulic transmission second output gear pair can be connected with the front sun gear (201).
7. The multi-mode mechatronic transmission of claim 6, wherein: double-ring transmission subassembly (800) includes double-ring transmission input shaft (802), be connected with preceding annular drive mechanism (803) and can be connected with the hydraulic transmission gear pair double-ring transmission input gear pair (808) on double-ring transmission input shaft (802), the output of preceding annular drive mechanism (803) is connected with back annular drive mechanism (804), the output of back annular drive mechanism (804) is connected with double-ring transmission output shaft (805), be connected with double-ring transmission output gear pair (807) on double-ring transmission output shaft (805), double-ring transmission output gear pair (807) can be connected with well sun gear (403).
8. The multi-mode mechatronic transmission of claim 5, wherein: the hydrostatic transmission assembly (300) further includes a first clutch (303), a second clutch (307), and a third clutch (308), the first clutch (303) for selectively connecting the input shaft (100) for common rotation with the hydrostatic transmission input shaft (302), the second clutch (307) for selectively connecting the hydrostatic transmission output shaft (309) for common rotation with the forward carrier (202), the third clutch (308) for selectively connecting the hydrostatic transmission output shaft (309) for common rotation with the forward sun gear (201).
9. The multi-mode mechatronic transmission of claim 8, wherein: the dual ring transmission assembly (800) further includes a fourth clutch (801) for selectively connecting the dual ring transmission input shaft (802) to the input shaft (100) for common rotation and a fifth clutch (806) for selectively connecting the dual ring output shaft (700) to the mid sun gear (403) for common rotation.
10. A multi-mode machine hydraulic transmission as claimed in any one of claims 2 to 4, wherein: the central planetary assembly (400) further comprising a sixth clutch (405), the sixth clutch (405) being for selectively connecting the central ring gear (401) to the central sun gear (403) for common rotation, the rear planet wheel assembly (500) further comprises a seventh clutch (502), an eighth clutch (504), a ninth clutch (503) and a tenth clutch (505), the seventh clutch (502) is for selectively connecting the sun gear (403) to the rear ring gear (501) for common rotation, the eighth clutch (504) for selectively connecting the mid-sun gear (403) to the rear planet carrier (506) for common rotation, the ninth clutch (503) is for selectively connecting the rear ring gear (501) to the output shaft (700) for common rotation, the tenth clutch (505) is for selectively connecting the rear planet carrier (506) to the output shaft (700) for common rotation.
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0563941A1 (en) * 1992-03-31 1993-10-06 Mazda Motor Corporation Power train for an automotive vehicle
US20160109003A1 (en) * 2014-10-17 2016-04-21 Allison Transmission, Inc. Split power continuously variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges
CN110953318A (en) * 2019-11-06 2020-04-03 江苏大学 Mechanical hydraulic composite transmission device and control method
CN111207198A (en) * 2020-01-20 2020-05-29 江苏大学 Multi-mode mechanical-hydraulic composite transmission device integrating gear, hydraulic pressure and metal belt
US20220042587A1 (en) * 2020-08-03 2022-02-10 Jiangsu University Gear-double ring-hydraulic hybrid transmission device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0563941A1 (en) * 1992-03-31 1993-10-06 Mazda Motor Corporation Power train for an automotive vehicle
US20160109003A1 (en) * 2014-10-17 2016-04-21 Allison Transmission, Inc. Split power continuously variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges
CN110953318A (en) * 2019-11-06 2020-04-03 江苏大学 Mechanical hydraulic composite transmission device and control method
CN111207198A (en) * 2020-01-20 2020-05-29 江苏大学 Multi-mode mechanical-hydraulic composite transmission device integrating gear, hydraulic pressure and metal belt
US20220042587A1 (en) * 2020-08-03 2022-02-10 Jiangsu University Gear-double ring-hydraulic hybrid transmission device

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