CN111322361B - Eight-gear transmission speed change control system - Google Patents

Eight-gear transmission speed change control system Download PDF

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Publication number
CN111322361B
CN111322361B CN201911200317.9A CN201911200317A CN111322361B CN 111322361 B CN111322361 B CN 111322361B CN 201911200317 A CN201911200317 A CN 201911200317A CN 111322361 B CN111322361 B CN 111322361B
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China
Prior art keywords
oil
clutch
gear
path
oil path
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CN201911200317.9A
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Chinese (zh)
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CN111322361A (en
Inventor
薛天宝
雷作钊
周荣斌
罗南昌
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Fujian Zhongwei Power Technology Co Ltd
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Fujian Zhongwei Power Technology Co Ltd
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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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/14—Fluid pressure control
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
    • F16H61/0009—Hydraulic control units for transmission control, e.g. assembly of valve plates or valve units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
    • F16H61/0265—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0221—Valves for clutch control systems; Details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0811—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts using unsynchronised clutches
    • 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
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three engaging means

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Transmission Device (AREA)

Abstract

The invention relates to a speed change control system of an eight-gear transmission, which comprises a controller, wherein the controller is connected with the eight-gear transmission, and the eight-gear transmission comprises an input shaft, an output shaft, a gear pair unit, a first intermediate shaft gear set, a second intermediate shaft gear set, a central shaft, an oil circuit structure and an oil circuit control system; the controller comprises a plurality of analog quantity output units, and the analog quantity output units are respectively connected with the first regulation and control unit, the second regulation and control unit and the third regulation and control unit; the controller is used for acquiring gear information, and controlling the analog quantity output unit to output different analog quantity control information to the first regulation and control unit, the second regulation and control unit and the third regulation and control unit according to the control corresponding relation between the prestored gear information and the analog quantity output unit. The invention realizes the purpose of automatic and quick gear shifting through the controller.

Description

Eight-gear transmission speed change control system
Technical Field
The invention relates to the field of transmission control systems, in particular to an eight-gear transmission speed change control system.
Background
Eight grades of derailleur can realize the change of eight fender position, changes through the fender position change of difference, can change the different torques of front and back input. Through the switching of different clutches of the transmission, the switching of different gears of the transmission can be realized. The existing proportional valves for closing different clutches can be opened manually, so that manual gear switching is realized. In order to achieve a fast automatic transmission gear shift, a gear control system of the transmission is required.
Disclosure of Invention
Therefore, an eight-gear transmission speed change control system needs to be provided to solve the problem that the existing transmission needs automatic quick gear shifting.
In order to achieve the above object, the inventor provides a speed change control system of an eight-gear transmission, which comprises a controller, wherein the controller is connected with the eight-gear transmission, and the eight-gear transmission comprises an input shaft, an output shaft, a gear pair unit, a first intermediate shaft gear set, a second intermediate shaft gear set, a central shaft, an oil way structure and an oil way control system;
the input shaft is provided with a first input gear, the output shaft is provided with a first output gear, the central shaft is provided with a first central gear and a second central gear, the driving part of the gear pair unit is arranged on the input shaft and/or the central shaft, and the gear pair unit is positioned between the first input gear and the first central gear;
the linkage part of the gear pair unit is arranged on a main shaft of a first intermediate shaft gear set, the first intermediate shaft gear set is used for being meshed with a first input gear, a driving part of the gear pair unit and a first central gear respectively to form gear pair transmission, and the second intermediate shaft gear set is used for being meshed with a second central gear and a first output gear respectively to form gear pair transmission;
the gear pair unit is used for transmitting the power of the input shaft to the first intermediate shaft gear set and/or transmitting the power on the first intermediate shaft gear set to the central shaft;
a first clutch is arranged on an input shaft between the first input gear and the gear pair unit, a first clutch end of the first clutch is arranged on the first input gear, and a second clutch end of the first clutch is arranged on the gear pair unit;
a second clutch is arranged on a central shaft between the gear pair unit and the first central gear, a first clutch end of the second clutch is arranged on the gear pair unit, and a second clutch end of the second clutch is arranged on the first central gear;
a third clutch is arranged on the output shaft between the second central gear and the first output gear, a first clutch end of the third clutch is arranged on the second central gear, and a second clutch end of the third clutch is arranged on the first output gear;
the oil path structure comprises a shell oil path, an input shaft oil path, an output shaft oil path, a central shaft oil path, a first clutch oil path, a second clutch oil path and a third clutch oil path, wherein the shell oil path is arranged in the shell, the input shaft oil path is arranged in the input shaft, and a first branch of the shell oil path is communicated with the input shaft oil path; the central shaft oil way is arranged in the central shaft, and a second branch of the shell oil way is communicated with the central shaft oil way; the output shaft oil path is arranged in the output shaft, and a third branch of the shell oil path is communicated with the output shaft oil path; the first clutch oil path is arranged in the first clutch, and the input shaft oil path is communicated with the first clutch oil path; the second clutch oil path is arranged in the second clutch, and the central shaft oil path is communicated with the second clutch oil path; the third clutch oil path is arranged in the third clutch, and the output shaft oil path is communicated with the third clutch oil path;
the oil circuit control system comprises a power unit, a first regulating unit, a second regulating unit and a third regulating unit, wherein the output end of the power unit is connected with a shell oil circuit pipeline, the first regulating unit is arranged on a pipeline between a first branch of a shell oil circuit and the power unit, the second regulating unit is arranged on a pipeline between a second branch of the shell oil circuit and the power unit, and the third regulating unit is arranged on a pipeline between a third branch of the shell oil circuit and the power unit; the first regulation and control unit is used for controlling the hydraulic oil pressure at two ends of the first clutch, the second regulation and control unit is used for controlling the hydraulic oil pressure at two ends of the second clutch, and the third regulation and control unit is used for controlling the hydraulic oil pressure at two ends of the third clutch;
the controller comprises a plurality of analog quantity output units, and the analog quantity output units are respectively connected with the first regulation and control unit, the second regulation and control unit and the third regulation and control unit in a one-to-one correspondence manner; the controller is used for acquiring gear information, and controlling the analog quantity output unit to output different analog quantity control information to the first regulation and control unit, the second regulation and control unit and the third regulation and control unit according to the control corresponding relation between the prestored gear information and the analog quantity output unit.
Further, the control corresponding relationship between the pre-stored gear information and the analog quantity output unit includes:
the prestored gear information is neutral gear, and the analog quantity output unit outputs the same analog quantity control information to the first regulation and control unit, the second regulation and control unit and the third regulation and control unit, so that the hydraulic oil pressure at two ends of the clutch controlled by each regulation and control unit is the same.
Furthermore, the housing oil path comprises a first double-hole conveying oil path, a second double-hole conveying oil path and a third double-hole conveying oil path, an oil inlet of the first double-hole conveying oil path, an oil inlet of the second double-hole conveying oil path and an oil inlet of the third double-hole conveying oil path are arranged on the outer side surface of the housing, an oil outlet of the first double-hole conveying oil path is arranged on the inner surface of the shaft hole of the input shaft, an oil outlet of the second double-hole conveying oil path is arranged on the inner surface of the shaft hole of the central shaft, and an oil outlet of the third double-hole conveying oil path is arranged on the inner surface of the shaft hole of the output shaft.
Further, the first clutch oil path comprises a first oil guide passage and a second oil guide passage;
the first oil guide channel is arranged between one side of the piston inner cavity of the clutch and the inner side surface of the inner hole of the clutch, and the second oil guide channel is arranged between the other side of the piston inner cavity of the clutch and the inner side surface of the inner hole of the clutch;
the second clutch oil path and the third clutch oil path are structurally identical to the first clutch oil path.
Furthermore, the first regulating and controlling unit comprises a first proportional valve, a second proportional valve, a first pressure detector and a second pressure detector, the first proportional valve is arranged on a pipeline between the shell oil path where the first oil guide channel is located and the power unit, an oil return port of the first proportional valve is connected with the oil storage tank pipe, the second proportional valve is arranged on a pipeline between the shell oil path where the second oil guide channel is located and the power unit, and an oil return port of the second proportional valve is connected with the oil storage tank pipe;
the first pressure detector is arranged on a pipeline between the first proportional valve and the first clutch, and the second pressure detector is arranged on a pipeline between the second proportional valve and the first clutch;
the second regulation and control unit and the third regulation and control unit are arranged in the same structure as the first regulation and control unit, the second regulation and control unit is arranged on a second clutch oil path, and the third regulation and control unit is arranged on a third clutch oil path.
Further, the first clutch includes a first clutch piece, a second clutch piece, and a piston unit;
the piston unit comprises a double-end piston body and a cavity, the cross section of the double-end piston body is I-shaped, one end of the double-end piston body is arranged in the cavity, the other end of the double-end piston body is positioned outside the cavity, the oil outlet of the first oil guide channel is arranged on one side of the cavity, and the oil outlet of the second oil guide channel is arranged on the other side of the cavity;
the first clutch block comprises a first friction plate group, the second clutch block comprises a second friction plate group, the first friction plate group is positioned on one side of the other end of the double-end piston body, the second friction plate group is positioned on the other side of the other end of the double-end piston body, the first clutch block and the second clutch block are arranged on a gear pair, and the double-end piston body is used for driving one group of the first friction plate group or the second friction plate group to be combined and the other group of the first friction plate group or the second friction plate group to be separated;
the second clutch and the third clutch are arranged in the same structure as the first clutch.
Furthermore, the input shaft oil path comprises a first conveying oil path and a second conveying oil path, an oil inlet of the first conveying oil path is communicated with one oil path of the first double-hole conveying oil path, an oil outlet of the first conveying oil path is communicated with the first oil guide path, an oil inlet of the second conveying oil path is communicated with the other oil path of the first double-hole conveying oil path, and an oil outlet of the second conveying oil path is communicated with the second oil guide path.
Furthermore, the center shaft oil path comprises a third conveying oil path and a fourth conveying oil path, an oil inlet of the third conveying oil path is communicated with one oil path of the second double-hole conveying oil path, an oil outlet of the third conveying oil path is communicated with one oil guide path of the second clutch oil path, an oil inlet of the fourth conveying oil path is communicated with the other oil path of the second double-hole conveying oil path, and an oil outlet of the fourth conveying oil path is communicated with the other oil guide path of the second clutch oil path.
Furthermore, the output shaft oil path comprises a fifth delivery oil path and a sixth delivery oil path, an oil inlet of the fifth delivery oil path is communicated with an oil path of the third double-hole delivery oil path, an oil outlet of the fifth delivery oil path is communicated with an oil guide path of the third clutch oil path, an oil inlet of the sixth delivery oil path is communicated with another oil path of the third double-hole delivery oil path, and an oil outlet of the sixth delivery oil path is communicated with another oil guide path of the third clutch oil path.
Further, the analog output unit is a current output unit or a voltage output unit.
Different from the prior art, the technical scheme has the following advantages: through the control corresponding relation between the gear information prestored in the controller and the analog quantity output unit, when the gear is required to be switched, the controller can output the analog quantity according to the corresponding relation. Thereby change the hydraulic pressure at the clutch both ends of regulation and control unit control, just can realize the drive to the clutch, realize the separation and reunion effect to change the switching action of different gear trains in the derailleur, thereby realize the operation of shifting gears, thereby realized the purpose of shifting gears through the controller is automatic fast.
Drawings
FIG. 1 is a schematic structural diagram of a shift control system according to an exemplary embodiment;
FIG. 2 is a diagrammatic illustration of eight speed transmission shifting in accordance with an exemplary embodiment;
FIG. 3 is a diagrammatic view of an eight speed transmission according to an exemplary embodiment;
FIG. 4 is a cross sectional view of an eight speed transmission according to an exemplary embodiment;
FIG. 5 is a block diagram of an eight speed transmission according to an exemplary embodiment;
FIG. 6 is a partial schematic illustration of an eight speed transmission according to an exemplary embodiment.
Description of reference numerals:
1. a controller; 2. an eight speed transmission; 3. a CPU; 4. an analog quantity output unit; 10. an input shaft; 11 a first input gear; 12. an input shaft oil path; 121. a first delivery oil path;
122. a second delivery oil path;
20. an output shaft; 21. a first output gear; 22. an output shaft oil path;
221. a fifth delivery oil path; 222. a sixth oil delivery passage;
30. a gear pair unit; 301. a common gear; 302. an input output gear;
40. a first countershaft gear set; 41. a transmission intermediate shaft; 42. a second input gear;
43. a central input gear;
50. a second countershaft gear set; 51. an output intermediate shaft; 52. a central output gear;
53. a second output gear;
60. a central shaft; 61. a first sun gear; 62. a second sun gear; 63. a central shaft oil path;
631. a third oil delivery path; 632. a fourth delivery oil path;
70. a first clutch; 71. a first clutch oil path; 712. a first oil guide passage;
713. a second oil guide passage; 72. a first clutch block; 73. a second clutch block; 74. a piston unit;
741. a double-ended piston body; 742 the cavity; 75. a first friction plate set; 76. a second friction plate set; 80. a second clutch; 81. a second clutch oil path;
90. a third clutch; 91. a third clutch oil path;
100. a housing; 101. a housing oil passage; 1011. a first double-hole oil delivery path;
1012. a second double-hole oil delivery path; 1013. a third double-hole oil delivery path;
01. a first seal ring; 02. a second seal ring; 03. and a third seal ring.
090. An oil circuit control system; 091. a power unit; 092. a first regulation unit;
093. a second regulatory unit; 094. an oil storage tank; 095. a filter; 096. a third regulatory unit; 0921. a first proportional valve; 0922. a second proportional valve; 0923. a first pressure detector; 0924. a second pressure detector.
Detailed Description
To explain technical contents, structural features, and objects and effects of the technical solutions in detail, the following detailed description is given with reference to the accompanying drawings in conjunction with the embodiments.
Referring to fig. 1 to 6, the present invention provides a gear shift control system for an eight-speed transmission, including a controller 1, where the controller 1 is connected to an eight-speed transmission 2, and the eight-speed transmission 2 includes an input shaft 10, an output shaft 20, a gear pair unit 30, a first countershaft gear set 40, a second countershaft gear set 50, a central shaft 60, an oil path structure, and an oil path control system 090;
the oil passageway control system includes a power unit 091, a first regulator unit 092, a second regulator unit 093, a third regulator unit 096, an oil storage tank 094, and a filter 095. An oil inlet of a shell oil path on the outer side of the shell is connected with a power unit through a pipe, and the power unit can be a gear pump or a hydraulic pump and the like to convey hydraulic oil. Two oil ducts are arranged in a first clutch oil path of the oil path structure, and the two oil ducts are respectively as follows: the first oil guide channel and the second oil guide channel. The first oil guide passage is used for conveying hydraulic oil to one side of the double-head piston body in the cavity of the first clutch, and the second oil guide passage is used for conveying hydraulic oil to the other side of the double-head piston body in the cavity of the first clutch. Therefore, when one side oil feed in the cavity, can promote the double-end piston body and remove for the cavity space of this side increases and increases the oil pressure, and the space of the opposite side in the relative cavity reduces, then needs to carry out the oil return. And each clutch is provided with two independent oil supply channels, so that hydraulic oil is respectively conveyed outside the shell through a pipeline. In the present embodiment, three clutches are provided, and all three clutches are switched double clutches, so that six independent pipelines are provided on the housing, and six independent branch pipelines are required for conveying hydraulic oil.
Specifically, in order to make be full of hydraulic oil in the oil circuit, reach the oil feed and can drive the effect that the double-end piston body removed. The first regulation unit in this embodiment includes a first proportional valve 0921, a second proportional valve 0922, a first pressure detector 0923, and a second pressure detector 0924, and the first and second proportional valves may be proportional pressure reducing valves. Two sections of pipelines are arranged between the oil storage tank and the shell, the front part of the pipeline is a main pipeline, and the rear part of the pipeline is four branch pipelines. The gear pump, the filter and the main way check valve are sequentially installed on the main way, the filter can be installed in a plurality of ways, and the branch check valve, the proportional valve and the pressure detector are sequentially installed on each branch pipeline.
Taking the first independent oil circuit that leads the oil duct place as an example, when carrying out the transport hydraulic oil, opening the gear pump and carrying the hydraulic oil in the batch oil tank to the filter in, the filter filters the large granule impurity in the hydraulic oil, for example dust, grit or oil block etc.. And then is conveyed to each branch pipeline through a main one-way valve. Hydraulic oil is conveyed to the oil way structure through the branch one-way valve, the first proportional valve and the first pressure detector on the branch pipeline again, and then the hydraulic oil is conveyed to one side in the cavity of the first clutch through the first oil guide channel. In the same way, the independent oil path where the second oil guide passage is located conveys the hydraulic oil to the oil path structure through the branch one-way valve, the second proportional valve and the second pressure detector on the other branch pipeline, and then conveys the hydraulic oil to the other side in the cavity of the first clutch through the second oil guide passage.
After the hydraulic oil enters the oil path structure, if the first clutch is controlled, the hydraulic oil sequentially passes through the shell oil path, the input shaft oil path and the first clutch oil path to reach the piston cavity of the first clutch.
And if the piston cavity of the first clutch returns oil, the oil is decompressed and returned through the proportional pressure reducing valve, the proportional pressure reducing valve can return oil according to the oil pressure, and the returned hydraulic oil is conveyed back to the oil storage tank. Meanwhile, the first pressure detector monitors the oil pressure on the first oil guide channel, namely when the oil pressure in the cavity of the first clutch is reduced, the first pressure detector feeds detected information back to the terminal, and the terminal can be a computer, a mobile phone or an industrial control mainframe box. And the oil return quantity of the first proportional valve is controlled through the terminal to process information, so that the oil channel structure of the first clutch is in a full oil state.
In a similar way, the second clutch is conveyed into the piston cavity through the central shaft oil path and the second clutch oil path, two proportional valves of the second regulating and controlling unit are used for oil supplement and oil return, pressure detection is carried out through the second pressure detector, and oil supplement or oil return cooperative adjustment is carried out on the oil path of the second clutch, so that the oil path is in a full oil state. And the third clutch is conveyed into the piston cavity through the output shaft oil way and the third clutch oil way, oil supplement and oil return are carried out by using two proportional valves of the third regulating and controlling unit, pressure detection is carried out by using a third pressure detector, and oil supplement or oil return cooperative adjustment is carried out on the oil way of the third clutch so that the oil way is in a full oil state. Because the first clutch, the second clutch and the third clutch have the same structure, and the first clutch oil circuit, the second clutch oil circuit and the third clutch oil circuit which are respectively arranged in the first clutch, the second clutch and the third clutch are also the same, and in addition, the second regulating and controlling unit and the third regulating and controlling unit are both arranged in the same structure as the first regulating and controlling unit, the second regulating and controlling unit can be used for carrying out the conveying control of the hydraulic oil on the second clutch, and the third regulating and controlling unit can be used for carrying out the conveying control of the hydraulic oil on the third clutch. Thereby achieving the purpose of controlling the clutch with zero waiting.
The existing controller is generally an intelligent control unit and can comprise a CPU3, and the CPU3 can store therein a control correspondence between gear information and an analog output unit. In order to realize the control of the speed changer regulating and controlling unit, the controller comprises a plurality of analog quantity output units 4 which are respectively connected with the first regulating and controlling unit, the second regulating and controlling unit and the third regulating and controlling unit; the controller is used for acquiring gear information, and controlling the analog quantity output unit to output different analog quantity control information to the first regulation and control unit, the second regulation and control unit and the third regulation and control unit according to the control corresponding relation between the prestored gear information and the analog quantity output unit. The controller is configured to acquire the gear information, where the gear information may be required gear information calculated by the controller according to an external input, or the unit information is directly sent to the controller by an external module. The analog quantity output unit may be a voltage output unit or a current output unit, corresponding to the output voltage or current. Thereby realizing the control of different types of regulating units. The analog quantity output unit can be constructed by an analog circuit, and after the analog quantity is output by the CPU, the analog quantity signal is amplified by the analog circuit, so that the output of the analog quantity with larger driving capability is realized. Or the analog output unit can be a single digital-to-analog chip, and after the digital quantity is output by the CPU, a signal with driving capability is output through the digital-to-analog chip. Finally, the control of the regulation and control unit is realized. After the controller controls the regulation and control unit, the hydraulic pressure at the two ends of the clutch controlled by the regulation and control unit can be changed, so that the clutch can be driven, the clutch effect is realized, the switching action of different gear sets in the transmission is changed, the gear shifting operation is realized, and the purpose of automatically and quickly shifting gears through the controller is realized.
Since the clutch of the present embodiment is a switching type dual clutch, if the hydraulic balance at both ends of the clutch is changed, the end with a small pressure is in an engaged state, and the other end is in a disengaged state. The hydraulic balance across the clutch is maintained, i.e. the pressure is the same, when neutral is required. When the acquired gear information is neutral, the controller controls the analog quantity output unit to output the same analog quantity control information to the regulation and control unit, so that the hydraulic oil pressures at the two ends of the clutch controlled by the regulation and control unit are the same, the clutch is located in the middle position, and the two ends of the clutch are in a separated state. In order to realize the neutral gear control, the controller stores the corresponding relation between the gear information of the neutral gear and the same analog quantity to be output by the analog quantity output unit in advance, such as a corresponding relation table. And then, in the control process, the rapid gear control can be realized only by reading the corresponding relation. When other gears are needed, one gear can be set to have one end of the hydraulic pressure at two ends of the clutch larger than the other end of the hydraulic pressure, and the other gear can be set to have the other end of the hydraulic pressure at two ends of the clutch larger than one end of the hydraulic pressure. When the pressure difference exists between the two ends of the clutch, namely one end of the clutch is in an engaged state, a gear condition is entered, and therefore gear switching of the controller is achieved. Two gears of one clutch can be changed, and eight gears can be changed by different combinations of three clutches of the eight-gear transmission, so that eight-gear switching is realized.
The first input gear 11 is mounted on the input shaft, the first output gear 21 is mounted on the output shaft, and the first sun gear 61 and the second sun gear 62 are mounted on the central shaft. The gear pair unit comprises a driving part and a linkage part, the driving part is arranged on the input shaft and/or the central shaft, and the linkage part is arranged on the main shaft of the first central shaft gear set, so that the driving part and the linkage part form a gear pair to transmit power. The central axis of the input shaft, the central axis of the output shaft and the central axis of the central shaft are collinear, the central axis of the main shaft of the first intermediate shaft gear set is parallel to the central axis of the input shaft, and the central axis of the main shaft of the second intermediate shaft gear set is parallel to the central axis of the output shaft in the same way, so that the length size of the transmission is reduced compared with the existing transmission in structural arrangement, the area of the cross section is not increased, the overall size of the transmission is reduced, the space for installing the transmission is saved, and the production cost of the transmission is reduced.
A first clutch 70 is provided on the input shaft between the first input gear and the gear sub unit for clutching the first input gear and the gear sub unit. A second clutch 80 is provided on the central shaft between the gear sub unit and the first sun gear, and is used for clutching the gear sub unit and the first sun gear. A third clutch 90 is arranged on the output shaft between the second sun gear and the first output gear, and is used for performing clutch operation on the second sun gear and the first output gear. Meanwhile, no matter the first clutch, the second clutch and the third clutch are in any closed state, the transmission only has one gear output, so that the only path of power in transmission is realized.
In this embodiment, the first clutch, the second clutch and the third clutch may be any clutch structure such as a friction clutch, a hydraulic torque converter (fluid coupling), a pneumatic clutch, a dog clutch, a synchronizer, or an electromagnetic clutch. Each clutch has two clutch ends, for example, the first clutch is operated to open or close the first input gear through the first clutch end, and the first clutch is operated to open or close the common gear 301 through the second clutch end, so as to realize the clutch operation of the two gear pairs.
In this embodiment, the first clutch includes a first clutch piece 72, a second clutch piece 73 and a piston unit 74, the piston unit includes a double-end piston body 741 and a cavity 742, the double-end piston body has an i-shaped cross section, and the double-end piston body is formed by combining three ring bodies, so that the double-end piston body is installed in the cavity, and the double-end piston body is controlled to move in the cavity by inputting hydraulic oil, thereby achieving a clutch operation in which one end of the clutch is in an engaged state and the other end of the clutch is in a disengaged state.
In the present embodiment, the first friction plate set 75 and the second friction plate set 76 are arranged in the same structure, and the components thereof may be a friction plate and a steel plate or a friction plate and a friction plate, and the friction plate and the steel plate are taken as an example in the present embodiment for illustration. Installing a friction plate on the clutch block, and installing a steel sheet on the outer side surface of the cavity; on the contrary, the friction plate can be arranged on the outer side surface of the cavity, the steel sheet is arranged on the clutch block, and then the mutual contact friction effect between the friction plate and the steel sheet is formed, so that the gear connected to the other end of the clutch block is subjected to clutch operation.
The oil path structure in this embodiment includes a housing oil path 101, an input shaft oil path 12, an output shaft oil path 22, a center shaft oil path 63, a first clutch oil path 71, a second clutch oil path 81, and a third clutch oil path 91, where the housing oil path is disposed in the housing, the input shaft oil path is disposed in the input shaft, and a first branch of the housing oil path is communicated with the input shaft oil path; the central shaft oil way is arranged in the central shaft, and a second branch of the shell oil way is communicated with the central shaft oil way; the output shaft oil circuit is arranged in the output shaft, and a third branch of the shell oil circuit is communicated with the output shaft oil circuit. The first clutch oil path is arranged in the first clutch, and the input shaft oil path is communicated with the first clutch oil path; the second clutch oil path is arranged in the second clutch, and the central shaft oil path is communicated with the second clutch oil path; the third clutch oil path is arranged in the third clutch, and the output shaft oil path is communicated with the third clutch oil path.
The housing oil paths include a first double-hole delivery oil path 1011, a second double-hole delivery oil path 1012, and a third double-hole delivery oil path 1013, the first clutch oil path includes a first oil guide channel 712 and a second oil guide channel 713, the input shaft oil path includes a first delivery oil path 121 and a second delivery oil path 122, the center shaft oil path includes a third delivery oil path 631 and a fourth delivery oil path 632, and the output shaft oil path includes a fifth delivery oil path 221 and a sixth delivery oil path 222. Specifically, hydraulic oil is injected into one side of the cavity through the first oil guide passage, and meanwhile hydraulic oil is also injected into the other side of the cavity through the second oil guide passage, so that the pressures of the two ends of the double-end piston body in the cavity are the same, the double-end piston body is kept balanced in the cavity, and an initial preparation state is achieved.
The oil inlet of the first oil conveying path is communicated with one oil duct of the first double-hole oil conveying path, the oil outlet of the first oil conveying path is communicated with the first oil guide duct, the oil inlet of the second oil conveying path is communicated with the other oil duct of the first double-hole oil conveying path, and the oil outlet of the second oil conveying path is communicated with the second oil guide duct. The oil inlet of the third oil conveying path is communicated with one oil duct of the second double-hole oil conveying path, the oil outlet of the third oil conveying path is communicated with one oil guide duct of the second clutch oil path, the oil inlet of the fourth oil conveying path is communicated with the other oil duct of the second double-hole oil conveying path, and the oil outlet of the fourth oil conveying path is communicated with the other oil guide duct of the second clutch oil path. The oil inlet of the fifth oil conveying path is communicated with one oil duct of the third double-hole oil conveying path, the oil outlet of the fifth oil conveying path is communicated with one oil guide duct of the third clutch oil path, the oil inlet of the sixth oil conveying path is communicated with the other oil duct of the third double-hole oil conveying path, and the oil outlet of the sixth oil conveying path is communicated with the other oil guide duct of the third clutch oil path.
In this embodiment, only one clutch is provided on the input shaft, so that only two oil passages are needed to convey hydraulic oil respectively. When the first clutch is subjected to clutch operation, hydraulic oil is input into the cavity of the first clutch through the shell oil path, the input shaft oil path and the first clutch oil path, and then the hydraulic oil is conveyed.
Specifically, two oil passages are formed among the shell, the input shaft and the first clutch. The first double-hole oil conveying path of the shell oil path is provided with two oil paths, hydraulic oil is conveyed to the input shaft through the first double-hole oil conveying path, the input shaft oil path is conveyed through the first oil conveying path and the second oil conveying path respectively and is in conduction connection with the two oil paths of the first double-hole oil conveying path respectively, the first clutch oil path is in conduction connection with the first oil conveying path through the first oil guide path, the second oil guide path is in conduction connection with the second oil conveying path and conveys the hydraulic oil to the two sides of the cavity respectively, and the purpose of conveying the hydraulic oil from the shell to the first clutch and the purpose of conveying the hydraulic oil into the second clutch are achieved. In a similar way, the oil path arrangement principle of the hydraulic oil transmission of the second clutch on the central shaft is the same, namely the hydraulic oil is transmitted to the cavity of the second clutch through the second double-hole transmission oil path of the shell oil path, the central shaft oil path and the second clutch oil path. The oil circuit that the hydraulic oil of the third clutch on the output shaft carried sets up the principle the same, carries oil circuit, output shaft oil circuit and third clutch oil circuit through the third diplopore of casing oil circuit promptly, carries hydraulic oil to the cavity of third clutch in.
Two annular oil inlet grooves are formed in the connecting position of a first double-hole oil conveying way of a shell oil way and an input shaft oil way, two sides of each oil inlet groove are sealed through a first sealing ring 01, namely the sealing rings are located between the shell and the input shaft for sealing, and each first double-hole oil conveying way is provided with one oil inlet groove for conducting connection. And the input shaft is connected with the inner hole of the first clutch in an interference fit manner, and meanwhile, an annular oil outlet groove is adopted, so that the oil path of the input shaft is respectively communicated with the first oil guide channel and the second oil guide channel, and then hydraulic oil is respectively conveyed to two sides of the cavity, and the purpose of controlling the double-head piston body to move in the cavity through the oil pressure of the hydraulic oil is achieved. The second sealing ring 02 is arranged at the joint of the second double-hole oil conveying way and the central shaft oil way, and the third sealing ring 03 is arranged at the joint of the third double-hole oil conveying way and the output shaft oil way. The arrangement structure of the second sealing ring and the third sealing ring is the same as that of the first sealing ring.
In this embodiment, the first clutch block is connected to the input gear of the input shaft, and the second clutch block is connected to the common gear, so that the first clutch can perform mutually exclusive clutch control on the first gear pair of the input shaft and the second gear pair of the common gear. In this embodiment, for example, the first oil guiding passage pushes the double-headed piston body to move toward the common gear after oil enters, and the second oil guiding passage pushes the double-headed piston body to move toward the first input gear after oil enters.
And hydraulic oil pumps can be used for conveying the hydraulic oil in the oil tank to different pipelines in the oil circuit in the transmission. For example, when the first gear pair needs to be in the engaged state, the hydraulic oil is delivered through the other oil passage of the first double-hole delivery oil passage, the second delivery oil passage of the input shaft oil passage and the route of the second oil guide passage, so that the double-headed piston body of the first and second clutches moves towards the first gear pair. The first friction plate group is pushed by the double-end piston body to perform combined friction, and power is transmitted to the first input gear from the input shaft through the first clutch block, so that the first gear pair is in a combined state, namely the first input gear is meshed with the second input gear, and the power is transmitted to the intermediate shaft from the input shaft. And at the moment, the first double clutch and the second gear pair are in an off state.
Similarly, when the second gear pair is in a closed state, the hydraulic oil is conveyed through the oil passage of the first double-hole conveying oil passage, the first conveying oil passage of the input shaft oil passage and the route of the first oil guide passage, so that the double-head piston body of the first clutch moves towards the second gear pair. The second friction plate group is pushed by the double-end piston body to perform combined friction, and power is transmitted to the common gear from the input shaft through the second clutch block, so that the second gear pair is in a combined state, namely the common gear is meshed with the input and output gears, and the power is transmitted to the intermediate shaft from the input shaft. At this time, the first clutch and the first gear pair are in a disengaged state.
Similarly, the second clutch is used in the same manner as the first clutch. The second clutch conveys the hydraulic oil to the second clutch through the second double-hole conveying oil path, the output shaft oil path and the second oil guide path, namely, the two oil paths of the second double-hole conveying oil path, the third conveying oil path and the fourth conveying oil path of the output shaft oil path and the two oil paths of the second oil guide path are respectively connected and communicated, so that two mutually independent oil conveying paths are formed, and the purpose of mutually exclusive clutch control of the second gear pair and the third gear pair is achieved.
Specifically, in this embodiment, the oil inlet of the first oil delivery path is communicated with one oil passage of the first dual-hole oil delivery path, the oil outlet of the first oil delivery path is communicated with the first oil guide passage, the oil inlet of the second oil delivery path is communicated with the other oil passage of the first dual-hole oil delivery path, and the oil outlet of the second oil delivery path is communicated with the second oil guide passage. Similarly, the oil inlet of the third oil conveying path is communicated with one oil duct of the second double-hole oil conveying path, the oil outlet of the third oil conveying path is communicated with the first oil guide duct of the second clutch oil path, the oil inlet of the fourth oil conveying path is communicated with the other oil duct of the second double-hole oil conveying path, and the oil outlet of the fourth oil conveying path is communicated with the second oil guide duct of the second clutch oil path. Therefore, each clutch is provided with two oil conveying pipelines which are independent from each other and used for conveying hydraulic oil.
All adopt in the oil circuit structure of transmission in this embodiment to be full of hydraulic oil state work, consequently only need toward the cavity after hydraulic oil of reinjection into again, can make the oil pressure in the cavity unbalance, and then drive the double-end piston body and remove in the cavity to drive friction through the double-end piston body and combine first or second friction piece group, reach the effect of separation and reunion. The preparation time for driving the double-head piston body to move is zero, the effect of waiting for clutch switching when the time is zero is achieved, and the waiting time of the clutch structure during clutch switching is shortened.
The first countershaft gear set in this embodiment includes a drive countershaft 41, a second input gear 42 and a central input gear 43, and the gear pair unit includes a common gear 301 and an input output gear 302, the input output gear being mounted on the drive countershaft, the second input gear and the central input gear being sequentially disposed on the drive countershaft, the second input gear being disposed in meshing engagement with the first input gear, and the central input gear being disposed in meshing engagement with the first central gear. The common gear is arranged on the input shaft and/or the central shaft, the common gear is positioned between the first input gear and the first central gear, the input and output gear is positioned between the second input gear and the central input gear, and the input and output gear is meshed with the common gear.
Specifically, the first transmission path is: the first input gear is operated in an on state through the first clutch, and the common gear is operated in an off state, so that the power of the input shaft is transmitted into the transmission intermediate shaft through the gear pair of the first input gear and the second input gear. In this embodiment, for example, the first oil guiding passage pushes the double-headed piston body to move toward the common gear after oil enters, and the second oil guiding passage pushes the double-headed piston body to move toward the first input gear after oil enters. Meanwhile, the second clutch is used for carrying out on-state operation on the common gear, and the first sun gear is used for carrying out off-state operation, so that the power on the transmission intermediate shaft is transmitted to the central shaft through the gear pair of the common gear and the input and output gear. In this embodiment, for example, after the oil is fed, one oil guide passage of the second clutch pushes the double-headed piston body to move toward the first sun gear, and then the other oil guide passage of the second clutch pushes the double-headed piston body to move toward the common gear after the oil is fed.
The second transmission path is as follows: the first input gear is operated in an on state through the first clutch, and the common gear is operated in an off state, so that the power of the input shaft is transmitted into the transmission intermediate shaft through the gear pair of the first input gear and the second input gear. In this embodiment, for example, the first oil guiding passage pushes the double-headed piston body to move toward the common gear after oil enters, and the second oil guiding passage pushes the double-headed piston body to move toward the first input gear after oil enters. Meanwhile, the second clutch is used for carrying out off-state operation on the common gear and carrying out on-state operation on the first sun gear, so that power on the transmission intermediate shaft is transmitted to the central shaft through the gear pair of the central input gear and the first sun gear. In this embodiment, for example, after the oil is fed, one oil guide passage of the second clutch pushes the double-headed piston body to move toward the common gear, and then the other oil guide passage of the second clutch pushes the double-headed piston body to move toward the first sun gear after the oil is fed.
The third transmission path is: the first input gear is operated in the disengaged state and the common gear is operated in the engaged state by the first clutch, so that the power of the input shaft is transmitted to the transmission intermediate shaft via the gear pair of the common gear and the input-output gear. In this embodiment, for example, the first oil guide channel pushes the double-end piston body to move toward the first input gear after oil enters, and the second oil guide channel pushes the double-end piston body to move toward the common gear after oil enters. Meanwhile, the second clutch is used for carrying out on-state operation on the common gear, and the first sun gear is used for carrying out off-state operation, so that the power on the transmission intermediate shaft is directly transmitted to the central shaft through the common gear. In this embodiment, for example, after the oil is fed, one oil guide passage of the second clutch pushes the double-headed piston body to move toward the first sun gear, and then the other oil guide passage of the second clutch pushes the double-headed piston body to move toward the common gear after the oil is fed.
The fourth transmission path is: the first input gear is operated to be in a disengaged state and the common gear is operated to be in an engaged state by the first clutch, while the first sun gear is operated to be in an engaged state by the second clutch and the common gear is operated to be in an disengaged state, thereby allowing the power of the input shaft to be directly transmitted to the center shaft. In this embodiment, for example, the first oil guide channel pushes the double-end piston body to move toward the first input gear after oil enters, and the second oil guide channel pushes the double-end piston body to move toward the common gear after oil enters. One oil guide passage of the second clutch pushes the double-end piston body to move towards the direction of the common gear after oil is fed, and the other oil guide passage of the second clutch pushes the double-end piston body to move towards the direction of the first central gear after oil is fed. That is, power is transmitted to the transmission intermediate shaft through the gear pair of the common gear and the input/output gear, and then transmitted to the central shaft through the gear pair of the central input gear and the first central gear.
Because the input and output gears are meshed with the common gear to form a gear pair, the second input gear is meshed with the first input gear to form a gear pair, the central input gear is meshed with the first central gear to form a gear pair, and the gear ratios of the three sets of gear pairs are different. Therefore, when power is transmitted to the central shaft, the rotating speeds of the central shaft are four, and the purpose of changing the rotating speeds of the three groups of gear pairs is achieved.
And hydraulic oil pumps can be used for conveying the hydraulic oil in the oil tank to different pipelines in the oil circuit in the transmission. For example, when the first gear pair needs to be in the engaged state, the hydraulic oil is conveyed through the other oil passage of the first dual-orifice conveying oil passage, the second conveying oil passage of the input shaft oil passage and the second oil guide passage, so that the double-headed piston body of the first and second clutches moves towards the first gear pair. The first friction plate group is pushed by the double-end piston body to perform combined friction, and power is transmitted to the first input gear from the input shaft through the first clutch block, so that the first gear pair is in a combined state, namely the first input gear is meshed with the second input gear, and the power is transmitted to the intermediate shaft from the input shaft. And at the moment, the first double clutch and the second gear pair are in an off state.
Similarly, when the second gear pair is in a closed state, the hydraulic oil is conveyed through the oil passage of the first double-hole conveying oil passage, the first conveying oil passage of the input shaft oil passage and the route of the first oil guide passage, so that the double-head piston body of the first clutch moves towards the second gear pair. The second friction plate group is pushed by the double-end piston body to perform combined friction, and power is transmitted to the common gear from the input shaft through the second clutch block, so that the second gear pair is in a combined state, namely the common gear is meshed with the input and output gears, and the power is transmitted to the intermediate shaft from the input shaft. At this time, the first clutch and the first gear pair are in a disengaged state.
Similarly, the second clutch and the third clutch are used in the same way as the first clutch and the second clutch.
Specifically, in this embodiment, the oil inlet of the first oil delivery path is communicated with one oil passage of the first dual-hole oil delivery path, the oil outlet of the first oil delivery path is communicated with the first oil guide passage, the oil inlet of the second oil delivery path is communicated with the other oil passage of the first dual-hole oil delivery path, and the oil outlet of the second oil delivery path is communicated with the second oil guide passage. Similarly, the oil inlet of the third oil conveying path is communicated with one oil duct of the second double-hole oil conveying path, the oil outlet of the third oil conveying path is communicated with the first oil guide duct of the second clutch oil path, the oil inlet of the fourth oil conveying path is communicated with the other oil duct of the second double-hole oil conveying path, and the oil outlet of the fourth oil conveying path is communicated with the second oil guide duct of the second clutch oil path. Therefore, each clutch is provided with two oil conveying pipelines which are independent of each other and used for conveying hydraulic oil.
In the embodiment, power on the central shaft is output through the second intermediate shaft gear set and the output shaft, or the output shaft is directly output, so that gear switching is realized. The second intermediate shaft gear set comprises an output intermediate shaft 51, a central output gear 52 and a second output gear 53, the central output gear and the second output gear are sequentially arranged on the output intermediate shaft, the central output gear is meshed with the second central gear, and the second output gear is meshed with the first output gear. A gear pair with a second central gear and a central output gear, and a gear pair with a second output gear and a first output gear. Thus, in conjunction with the second sun gear on the central shaft, there are two paths for power transmission between the second countershaft gearset and the output shaft.
Specifically, because the second sun gear is always in meshed transmission with the sun output gear, the output intermediate shaft of the third clutch can be driven to rotate no matter the third clutch is in any state. The first transmission path is therefore: the second central gear is operated in an on state through the third clutch, and when the first output gear is operated in an off state, the power on the central shaft is directly transmitted to the output shaft. The second transmission path is as follows: when the third clutch is used for operating the second sun gear in an off state and the first output gear is used for operating the first output gear in an on state, the power on the second intermediate shaft gear set is transmitted to the output shaft through the gear pair of the second output gear and the first output gear. And because the gear ratio of the second sun gear to the sun output gear is different from the gear ratio of the second output gear to the first output gear, the output shaft has two rotation speeds for switching. The oil inlet modes of the two oil guide passages of the third clutch refer to the oil inlet modes of the oil guide passages of the first clutch and the second clutch.
Through the above, it can be known that five or six gear pairs can be arranged in the whole transmission, the gear ratios of any two gear pairs of the five or six gear pairs are not equal, and the gear ratios in the embodiment are the gear ratios of the driving gear and the driven gear, so that the output shaft has eight rotational transformations by combining the four rotational speed switching of the middle input shaft, the first intermediate shaft gear set and the central shaft, the purpose that the rotational speed of the input shaft is not equal to the rotational speed of the output shaft is achieved, and the whole transmission achieves the effect of switching eight gears.
In the above embodiments, the number of the transmission intermediate shaft and the output intermediate shaft may be plural, such as two, three, or four. The plurality of transmission intermediate shafts and the plurality of output intermediate shafts can be respectively arranged around the input shaft and the output shaft, for example, the two transmission intermediate shafts can be respectively arranged at the upper position and the lower position of the input shaft, the two output intermediate shafts can be respectively arranged at the upper position and the lower position of the output shaft, and the plurality of transmission intermediate shafts or the plurality of output intermediate shafts have the same structure, for example, the same gear is arranged. Therefore, the loads of the input shaft and the output shaft can be distributed through the plurality of transmission intermediate shafts and the output intermediate shafts, and the bending strength of the input shaft, the transmission intermediate shafts, the output intermediate shafts and the output shaft is enhanced, so that the bearing capacity of the input shaft and the output shaft is improved, and the purpose of high load is achieved.
The embodiment further includes a housing 100, and the housing hermetically accommodates the input shaft, the output shaft, the central shaft, the first intermediate shaft gear set, the second intermediate shaft gear set, and the gear pair on the input shaft, the output shaft, and the central shaft. Prevent external dust, steam and the like from entering the shell, and prolong the service life of the transmission.
It should be noted that, although the above embodiments have been described herein, the invention is not limited thereto. Therefore, based on the innovative concepts of the present invention, the technical solutions of the present invention can be directly or indirectly applied to other related technical fields by making changes and modifications to the embodiments described herein, or by using equivalent structures or equivalent processes performed in the content of the present specification and the attached drawings, which are included in the scope of the present patent.

Claims (9)

1. An eight-gear transmission speed change control system comprises a controller, wherein the controller is connected with an eight-gear transmission, and the eight-gear transmission speed change control system is characterized in that:
the eight-gear transmission comprises an input shaft, an output shaft, a gear pair unit, a first intermediate shaft gear set, a second intermediate shaft gear set, a central shaft, an oil path structure and an oil path control system;
the input shaft is provided with a first input gear, the output shaft is provided with a first output gear, the central shaft is provided with a first central gear and a second central gear, the driving part of the gear pair unit is arranged on the input shaft and/or the central shaft, and the gear pair unit is positioned between the first input gear and the first central gear;
the linkage part of the gear pair unit is arranged on a main shaft of a first intermediate shaft gear set, the first intermediate shaft gear set is used for being meshed with a first input gear, a driving part of the gear pair unit and a first central gear respectively to form gear pair transmission, and the second intermediate shaft gear set is used for being meshed with a second central gear and a first output gear respectively to form gear pair transmission;
the gear pair unit is used for transmitting the power of the input shaft to the first intermediate shaft gear set and/or transmitting the power on the first intermediate shaft gear set to the central shaft;
a first clutch is arranged on an input shaft between the first input gear and the gear pair unit, a first clutch end of the first clutch is arranged on the first input gear, and a second clutch end of the first clutch is arranged on the gear pair unit;
a second clutch is arranged on a central shaft between the gear pair unit and the first central gear, a first clutch end of the second clutch is arranged on the gear pair unit, and a second clutch end of the second clutch is arranged on the first central gear;
a third clutch is arranged on the output shaft between the second central gear and the first output gear, a first clutch end of the third clutch is arranged on the second central gear, and a second clutch end of the third clutch is arranged on the first output gear;
the oil path structure comprises a shell oil path, an input shaft oil path, an output shaft oil path, a central shaft oil path, a first clutch oil path, a second clutch oil path and a third clutch oil path, wherein the shell oil path is arranged in the shell, the input shaft oil path is arranged in the input shaft, and a first branch of the shell oil path is communicated with the input shaft oil path; the central shaft oil way is arranged in the central shaft, and a second branch of the shell oil way is communicated with the central shaft oil way; the output shaft oil path is arranged in the output shaft, and a third branch of the shell oil path is communicated with the output shaft oil path; the first clutch oil path is arranged in the first clutch, and the input shaft oil path is communicated with the first clutch oil path; the second clutch oil path is arranged in the second clutch, and the central shaft oil path is communicated with the second clutch oil path; the third clutch oil path is arranged in the third clutch, and the output shaft oil path is communicated with the third clutch oil path;
the first clutch oil path comprises a first oil guide passage and a second oil guide passage;
the first oil guide channel is arranged between one side of the piston inner cavity of the clutch and the inner side surface of the inner hole of the clutch, and the second oil guide channel is arranged between the other side of the piston inner cavity of the clutch and the inner side surface of the inner hole of the clutch;
the oil circuit control system comprises a power unit, a first regulating unit, a second regulating unit and a third regulating unit, wherein the output end of the power unit is connected with a shell oil circuit pipeline, the first regulating unit is arranged on a pipeline between a first branch of a shell oil circuit and the power unit, the second regulating unit is arranged on a pipeline between a second branch of the shell oil circuit and the power unit, and the third regulating unit is arranged on a pipeline between a third branch of the shell oil circuit and the power unit; the first regulating and controlling unit is used for controlling the hydraulic oil pressure at two ends of the first clutch, the second regulating and controlling unit is used for controlling the hydraulic oil pressure at two ends of the second clutch, and the third regulating and controlling unit is used for controlling the hydraulic oil pressure at two ends of the third clutch;
the controller comprises a plurality of analog quantity output units, and the analog quantity output units are respectively connected with the first regulation and control unit, the second regulation and control unit and the third regulation and control unit in a one-to-one correspondence manner; the controller is used for acquiring gear information, and controlling the analog quantity output unit to output different analog quantity control information to the first regulation and control unit, the second regulation and control unit and the third regulation and control unit according to the control corresponding relation between the prestored gear information and the analog quantity output unit;
the first clutch comprises a first clutch block, a second clutch block and a piston unit;
the piston unit comprises a double-end piston body and a cavity, the cross section of the double-end piston body is I-shaped, one end of the double-end piston body is arranged in the cavity, the other end of the double-end piston body is positioned outside the cavity, the oil outlet of the first oil guide channel is arranged on one side of the cavity, and the oil outlet of the second oil guide channel is arranged on the other side of the cavity;
the first clutch block comprises a first friction plate group, the second clutch block comprises a second friction plate group, the first friction plate group is positioned on one side of the other end of the double-end piston body, the second friction plate group is positioned on the other side of the other end of the double-end piston body, the first clutch block and the second clutch block are arranged on a gear pair, and the double-end piston body is used for driving one group of the first friction plate group or the second friction plate group to be combined and the other group of the first friction plate group or the second friction plate group to be separated;
the second clutch and the third clutch are arranged in the same structure as the first clutch.
2. The eight speed transmission shift control system according to claim 1, wherein: the control corresponding relation between the pre-stored gear information and the analog quantity output unit comprises the following steps:
the prestored gear information is neutral gear, and the analog quantity output unit outputs the same analog quantity control information to the first regulation and control unit, the second regulation and control unit and the third regulation and control unit, so that the hydraulic oil pressure at two ends of the clutch controlled by each regulation and control unit is the same.
3. The eight speed transmission shift control system according to claim 1, characterized in that: the oil way of the shell comprises a first double-hole conveying oil way, a second double-hole conveying oil way and a third double-hole conveying oil way, wherein an oil inlet of the first double-hole conveying oil way, an oil inlet of the second double-hole conveying oil way and an oil inlet of the third double-hole conveying oil way are arranged on the outer side surface of the shell, an oil outlet of the first double-hole conveying oil way is arranged on the inner surface of a shaft hole of the input shaft, an oil outlet of the second double-hole conveying oil way is arranged on the inner surface of the shaft hole of the central shaft, and an oil outlet of the third double-hole conveying oil way is arranged on the inner surface of the shaft hole of the output shaft.
4. The eight speed transmission shift control system according to claim 3, wherein:
and the second clutch oil path and the third clutch oil path are structurally identical to the first clutch oil path.
5. The eight-speed transmission speed change control system according to claim 4, wherein the first regulating and controlling unit comprises a first proportional valve, a second proportional valve, a first pressure detector and a second pressure detector, the first proportional valve is arranged on a pipeline between a housing oil path where the first oil guide path is located and the power unit, an oil return port of the first proportional valve is connected with the oil storage tank pipe, the second proportional valve is arranged on a pipeline between the housing oil path where the second oil guide path is located and the power unit, and an oil return port of the second proportional valve is connected with the oil storage tank pipe;
the first pressure detector is arranged on a pipeline between the first proportional valve and the first clutch, and the second pressure detector is arranged on a pipeline between the second proportional valve and the first clutch;
the second regulation and control unit and the third regulation and control unit are arranged in the same structure as the first regulation and control unit, the second regulation and control unit is arranged on a second clutch oil path, and the third regulation and control unit is arranged on a third clutch oil path.
6. The eight speed transmission shift control system according to claim 4, wherein: the input shaft oil path comprises a first conveying oil path and a second conveying oil path, an oil inlet of the first conveying oil path is communicated with one oil path of the first double-hole conveying oil path, an oil outlet of the first conveying oil path is communicated with the first oil guide path, an oil inlet of the second conveying oil path is communicated with the other oil path of the first double-hole conveying oil path, and an oil outlet of the second conveying oil path is communicated with the second oil guide path.
7. The eight speed transmission shift control system according to claim 4, wherein: the central shaft oil way comprises a third conveying oil way and a fourth conveying oil way, an oil inlet of the third conveying oil way is communicated with one oil way of the second double-hole conveying oil way, an oil outlet of the third conveying oil way is communicated with one oil guide way of the second clutch oil way, an oil inlet of the fourth conveying oil way is communicated with the other oil way of the second double-hole conveying oil way, and an oil outlet of the fourth conveying oil way is communicated with the other oil guide way of the second clutch oil way.
8. The eight speed transmission shift control system according to claim 4, wherein: the output shaft oil path comprises a fifth conveying oil path and a sixth conveying oil path, an oil inlet of the fifth conveying oil path is communicated with one oil path of the third double-hole conveying oil path, an oil outlet of the fifth conveying oil path is communicated with one oil guide path of the third clutch oil path, an oil inlet of the sixth conveying oil path is communicated with the other oil path of the third double-hole conveying oil path, and an oil outlet of the sixth conveying oil path is communicated with the other oil guide path of the third clutch oil path.
9. The eight speed transmission shift control system according to claim 1, wherein: the analog quantity output unit is a current output unit or a voltage output unit.
CN201911200317.9A 2019-11-29 2019-11-29 Eight-gear transmission speed change control system Active CN111322361B (en)

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Application Number Priority Date Filing Date Title
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Application Number Priority Date Filing Date Title
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201687901U (en) * 2010-05-27 2010-12-29 亢兆兆 Gear transmission mechanism and gear transmission system
CN102537268B (en) * 2012-01-13 2014-09-03 杭州祥龙钻探设备有限公司 Hydraulic clutching and gear-shifting transmission case of coal mine gallery drilling machine
CN104343959A (en) * 2013-07-23 2015-02-11 重庆长安汽车股份有限公司 Hydraulic control device for dual-clutch automatic transmission
JP6070861B2 (en) * 2013-11-29 2017-02-01 アイシン・エィ・ダブリュ株式会社 Power transmission device
DE112014006297A5 (en) * 2014-01-29 2016-11-03 Magna powertrain gmbh & co kg Change gear for the realization of at least eight forward gears
CN107795643B (en) * 2017-10-23 2020-03-31 山东迈克拉克工程机械有限公司 Speed changer
CN110259892A (en) * 2019-06-27 2019-09-20 贺宏良 More bidirectional clutch automatic gear-box and the car body that the gearbox is set

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