CN110469649B - Electrohydraulic control gear shifting gearbox - Google Patents
Electrohydraulic control gear shifting gearbox Download PDFInfo
- Publication number
- CN110469649B CN110469649B CN201910832159.2A CN201910832159A CN110469649B CN 110469649 B CN110469649 B CN 110469649B CN 201910832159 A CN201910832159 A CN 201910832159A CN 110469649 B CN110469649 B CN 110469649B
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- gear
- shaft
- piston
- valve core
- locking
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Classifications
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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
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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
- F16H48/00—Differential gearings
- F16H48/12—Differential gearings without gears having orbital motion
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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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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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
- 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
- F16H61/18—Preventing unintentional or unsafe shift, e.g. preventing manual shift from highest gear to reverse gear
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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
- 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
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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
- F16H2047/025—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the fluid gearing comprising a plurality of pumps or motors
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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
- 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
- F16H61/18—Preventing unintentional or unsafe shift, e.g. preventing manual shift from highest gear to reverse gear
- F16H2061/185—Means, e.g. catches or interlocks, for preventing unintended shift into reverse gear
Abstract
The invention discloses an electrohydraulic control gear shifting gearbox which comprises a hydraulic gear shifting system, a power input system, a two-shaft and a power output system, wherein two ends of the two-shaft are both rotationally connected with a shell, a first-gear driven gear, a gear hub and a second-gear driven gear are arranged on the two-shaft, the first-gear driven gear and the second-gear driven gear are idler gears, the gear hub is in transmission connection with the two-shaft, the first-gear driven gear and the second-gear driven gear are in transmission connection with the power input system, the two-shaft is in transmission connection with the power output system, a sliding meshing transmission piece is meshed with the gear hub, the sliding meshing transmission piece is used for transmitting the power of the first-gear driven gear or the second-gear driven gear to the gear hub or disconnecting the transmission connection of the gear hub, and the hydraulic gear shifting system is used for enabling the sliding meshing transmission piece to axially reciprocate along the two-shaft. The electrohydraulic control gear shifting gearbox provided by the invention is simple to operate, and is capable of directly shifting gears without selecting gears, shortening the gear shifting time and reducing the power loss.
Description
Technical Field
The invention relates to the technical field of gearboxes, in particular to an electrohydraulic control gear shifting gearbox.
Background
At present, the agricultural harvesting machine gearbox in the prior art generally adopts a mechanical manual gear shifting mode, namely a mode of a mechanical handle, a pull rod or a mechanical handle and a pull wire, and the gear shifting mode has the problems of difficult adjustment, high labor intensity and the like, and particularly in the middle-area, frequent turning and turning are required, and frequent gear shifting is required, so that the labor intensity of a manipulator is increased; during the use process, the gear shifting mechanism needs to be frequently adjusted along with the abrasion of parts, and if the gear shifting mechanism is not timely adjusted, secondary faults such as abrasion of a meshing sleeve, abrasion of a gear shifting gear and the like can be caused; the mechanical gear shifting mode generally needs to carry out the gear selecting and shifting processes after clutch, so that the gear shifting time is increased, and the energy consumption and the waste are caused.
Disclosure of Invention
The invention aims to provide an electrohydraulic control gear shifting gearbox which is simple to operate, convenient to maintain, high in reliability, capable of realizing direct gear shifting without gear selection, shortening gear shifting time, reducing power loss in the gear shifting process and improving power performance, fuel economy and driving comfort.
In order to achieve the above purpose, the invention adopts the following technical scheme:
the invention discloses an electrohydraulic control gear shifting gearbox which comprises a hydraulic gear shifting system, a shell, a power input system, two shafts, a sliding engagement transmission piece and a power output system, wherein two ends of each two shafts are rotationally connected with the shell, a first-gear driven gear, a gear hub and a second-gear driven gear are sequentially arranged on each two shafts along the axial direction of each two shafts, each first-gear driven gear and each second-gear driven gear is an idler gear, each gear hub is in transmission connection with each two shafts, each first-gear driven gear and each second-gear driven gear are in transmission connection with the power input system, each two shafts are in transmission connection with the power output system, each hydraulic gear shifting system is fixedly connected with the shell, and each sliding engagement transmission piece is meshed with each gear hub;
the hydraulic gear shifting system is used for driving the sliding engagement transmission piece to axially reciprocate along the two shafts so that the sliding engagement transmission piece is only engaged with the gear hub to realize neutral gear, or the sliding engagement transmission piece is simultaneously engaged with the gear hub and the first-gear driven gear to realize first gear, or the sliding engagement transmission piece is simultaneously engaged with the gear hub and the second-gear driven gear to realize second gear.
The beneficial effects of the invention are as follows: the power input system transmits power to a first-gear driven gear and a second-gear driven gear respectively, when the first-gear driven gear and the second-gear driven gear are in a neutral state, the sliding meshing transmission piece is meshed with the gear hub only, because the first-gear driven gear and the second-gear driven gear are idle gears, when the sliding meshing transmission piece is not meshed with the first-gear driven gear or the second-gear driven gear, the second shaft does not output power, the power input system stops power input when gear shifting is needed, the hydraulic gear shifting system drives the sliding meshing transmission piece to move along the axial direction of the second shaft so as to drive the sliding meshing transmission piece to move forwards and backwards along the second shaft, when the sliding meshing transmission piece is meshed with the first-gear driven gear and the gear hub simultaneously, the first-gear shifting is completed, the power of the first-gear driven gear is transmitted to the gear hub through the sliding meshing transmission piece, the gear hub is in transmission connection with the second shaft, and the gear hub drives the second shaft to rotate, and the second shaft is in transmission connection with the power output system, and at the moment, the power is output according to the speed of the first gear through the power output system; when the sliding engagement transmission piece is engaged with the second-gear driven gear and the gear hub, the second-gear shifting is completed, the power input system is started after the gear shifting is completed, the power of the second-gear driven gear is transmitted to the gear hub through the sliding engagement transmission piece, the gear hub drives the two shafts to rotate, the power is transmitted according to the speed of the second gear through the power output system, the sliding engagement transmission piece is driven to reciprocate through the hydraulic gear shifting system, the operation is simple, the maintenance is convenient, the reliability is high, the direct gear shifting without gear selecting process is realized, the gear shifting time is shortened, the power loss in the gear shifting process is reduced, and the power performance, the fuel economy and the driving comfort are improved.
Further, the hydraulic gear shifting system comprises a first cylinder body, a second cylinder body, a first piston assembly, a second piston assembly, a shifting fork and a fork shaft, wherein the first cylinder body and the second cylinder body are oppositely arranged on two sides of the shell, the first piston assembly is slidably arranged in the first cylinder body and divides the inner cavity of the first cylinder body into a first oil cavity and a first fork shaft cavity, the first oil cavity is provided with a first oil inlet, the second piston assembly is slidably arranged in the second cylinder body and divides the inner cavity of the second cylinder body into a second oil cavity and a second fork shaft cavity, the second oil cavity is provided with a second oil inlet, two ends of the fork shaft are slidably arranged in the first fork shaft cavity and the second fork shaft cavity respectively, the end part of the fork shaft in the first fork shaft cavity is in butt joint with the first piston assembly, the end part of the fork shaft in the second fork shaft cavity is in butt joint with the second piston assembly, the fork shaft is slidably connected with the shell and is parallel to the shifting fork shaft and is in parallel to the shifting fork shaft and is fixedly engaged with the reciprocating part in the shell.
The beneficial effects of adopting the further scheme are as follows: the hydraulic oil is injected into the first oil cavity through the first oil inlet, so that the first piston assembly pushes the fork shaft and the shifting fork to move towards the second cylinder body, the hydraulic oil is injected into the second mailbox through the second oil inlet, the second piston assembly pushes the fork shaft and the shifting fork to move towards the second cylinder body, the shifting fork drives the sliding engagement transmission piece to axially reciprocate along the two shafts, gear shifting is realized, the whole process is easy and convenient to operate, direct gear shifting without gear selection is realized, the gear shifting time is shortened, the power loss in the gear shifting process is reduced, the reliability is high, and the economy is good.
Further, the power input system is provided with a hydraulic motor, the output end of the hydraulic motor is in transmission connection with the first-gear driven gear and the second-gear driven gear, a first motor connecting port is formed in the middle of the first cylinder body, a second motor connecting port is formed in the middle of the second cylinder body, the first motor connecting port and the second motor connecting port are both communicated with the hydraulic motor, the first piston assembly is provided with a first piston oil duct, and the second piston assembly is provided with a second piston oil duct;
when a first gear is engaged, the second oil cavity is communicated with the second motor connecting port through the second piston oil duct;
When the second gear is engaged, the first oil cavity is communicated with the first motor connection port through the first piston oil duct.
The beneficial effects of adopting the further scheme are as follows: when the gear is shifted, the hydraulic motor stops power input, before the gear shifting is completed, part of hydraulic oil flows into the hydraulic motor through the first motor connector or the second motor connector, the hydraulic motor is driven to drive a shaft to rotate by a certain angle, so that the sliding engagement transmission piece can smoothly cut into the combination teeth of the first-gear driven gear or the second-gear driven gear and is engaged with the first-gear driven gear or the second-gear driven gear, the phenomenon that the sliding engagement transmission piece and the first-gear driven gear or the second-gear driven gear are in tooth-to-tooth is avoided in the moving process of the sliding engagement transmission piece, engagement cannot be completed, and the phenomenon that the gear is not hung up is avoided.
Further, the first piston assembly comprises a first piston and a first valve core, the first piston is arranged in the first cylinder body in a sliding manner and divides the inner cavity of the first cylinder body into a first oil cavity and a first fork shaft cavity, the first piston is provided with a first valve core mounting hole penetrating through two ends of the moving direction of the first piston, the first valve core is arranged in the first valve core mounting hole in a penetrating manner, the first piston is provided with a first piston assembly hole, the first valve core is provided with a first valve core groove, and in a second gear, the first piston assembly hole is communicated with the first motor connection port and the first valve core groove is communicated with the first oil cavity, and the first valve core groove is communicated with the first piston assembly hole to form the first piston oil duct;
The second piston assembly comprises a second piston and a second valve core, the second piston is arranged in the second cylinder body in a sliding mode, the second cylinder body inner cavity is divided into a second oil cavity and a second fork shaft cavity, the second piston is provided with a second valve core mounting hole penetrating through two ends of the second piston in the moving direction, the first valve core penetrates through the first valve core mounting hole, the second piston is provided with a second piston hole, the second valve core is provided with a second valve core groove, when the first gear is hung, the second piston hole is communicated with the second motor connecting port, the second valve core groove is communicated with the second oil cavity, and the second valve core groove is communicated with the second piston hole to form a second piston oil duct.
The beneficial effects of adopting the further scheme are as follows: before the sliding engagement transmission piece reaches the end part of the first-gear driven gear or the second-gear driven gear, hydraulic oil in a hydraulic gear shifting system cannot enter a hydraulic motor, a first piston oil duct and a second piston oil duct are blocked, hydraulic oil leakage in a first oil cavity and a second oil cavity is reduced, enough thrust is kept in the first oil cavity or the second oil cavity to push a fork shaft and a shifting fork to move, and the shifting fork drives the sliding engagement transmission piece to reach the end part of the first-gear driven gear or the second-gear driven gear, and the first piston oil duct or the second piston oil duct is communicated with the hydraulic motor, so that the hydraulic oil enters the hydraulic motor to drive the first shaft to rotate.
Further, the device also comprises a first guide positioning sleeve and a second guide positioning sleeve, wherein the first guide positioning sleeve is fixed at one end, close to the inner cavity of the shell, in the first cylinder body, the second guide positioning sleeve is fixed at one end, close to the inner cavity of the shell, in the second cylinder body, the fork shaft is arranged in the first guide positioning sleeve and the second guide positioning sleeve in a sliding manner, the first valve core is arranged in the first valve core mounting hole in a sliding manner, and the second valve core is arranged in the second valve core mounting hole in a sliding manner;
when a second gear is engaged, the end part of the first piston is abutted with the first guide positioning sleeve, the first valve core continuously pushes the fork shaft to move so that the sliding engagement transmission piece is engaged with the second gear driven gear, and the first valve core groove is disconnected with the first oil cavity;
when a first gear is engaged, the end part of the second piston is abutted with the second guide positioning sleeve, the second valve core continuously pushes the fork shaft to move so that the sliding engagement transmission piece is engaged with the first gear driven gear, and the second valve core groove is disconnected with the second oil cavity.
The beneficial effects of adopting the further scheme are as follows: the first valve core slides in the first piston, when the first piston moves to be abutted against the first guide positioning sleeve, the first piston oil duct is communicated with the first oil cavity and the first motor connecting port, the first valve core continues to move to finish gear shifting, and after the first valve core moves, the first valve core groove is disconnected from the first oil cavity and does not feed oil into the hydraulic motor; or the second valve core slides in the second piston, when the second piston moves to be in butt joint with the second guide positioning sleeve, the second piston oil duct is communicated with the second oil cavity and the second motor connecting port, the second valve core continues to move to finish gear shifting, and after the second valve core moves, the second valve core groove is disconnected from the second oil cavity, and oil is not fed into the hydraulic motor any more.
Further, the locking device also comprises a locking ball, wherein a first locking hole, a second locking hole and a third locking hole are sequentially formed in the outer wall of the fork shaft along the axial direction, a locking channel for the locking ball to move is formed in the sliding connection part of the shell and the fork shaft, the lower end of the locking channel is opened, and the locking ball is elastically limited in the locking channel;
when the second gear is engaged, the lower end of the locking channel is opposite to the first locking hole, the lower part of the locking ball is embedded into the first locking hole, and the upper part of the locking ball is arranged in the locking channel;
when the gear is engaged, the lower end of the locking channel is opposite to the second locking hole, the lower part of the locking ball is embedded into the second locking hole, and the upper part of the locking ball is arranged in the locking channel;
when a first gear is engaged, the lower end of the locking channel is opposite to the third locking hole, the lower part of the locking ball is embedded into the third locking hole, and the upper part of the locking ball is arranged in the locking channel.
The beneficial effects of adopting the further scheme are as follows: after the gear shift is completed, the lower part of the locking ball is embedded into the corresponding locking hole and matched with the locking channel, so that the fork shaft can be prevented from moving, the sliding engagement transmission piece is kept to be engaged with the corresponding part, and the random movement of the fork shaft in a non-gear shift state is avoided.
Further, the power output system comprises three shafts, three-shaft normal gears, three-shaft final drive gears and a differential mechanism, wherein the three shafts are parallel to the two shafts, two ends of the three shafts are rotationally connected with the shell, the three-shaft normal gears and the three-shaft final drive gears are fixedly connected with the three shafts, the two shafts are also coaxially and fixedly connected with the two-shaft normal gears, the three-shaft normal gears are meshed with the two-shaft normal gears, the three-shaft final drive gears are meshed with an input gear of the differential mechanism, and power input by the power input system is output through the differential mechanism.
The beneficial effects of adopting the further scheme are as follows: the power of the two axles is transmitted to the three axles through the two-axle normal-fit gear and the three-axle normal-fit gear, and then transmitted to the differential mechanism for output through the three axles, so that the left and right driving wheels of the automobile can rotate at different rotation speeds.
Further, the differential mechanism further comprises a first brake and a second brake, the differential mechanism is provided with a first output shaft and a second output shaft, the first output shaft and the second output shaft are respectively and rotatably connected with two opposite sides of the shell, the first brake and the second brake are respectively arranged on two opposite sides of the shell, the first brake is used for braking the first output shaft, and the second brake is used for braking the second output shaft.
The beneficial effects of adopting the further scheme are as follows: the two output shafts of the differential can be braked separately.
Further, the three-shaft brake further comprises a third brake, wherein the third brake is arranged on the shell at one end of the three shafts and is used for braking the three shafts.
The beneficial effects of adopting the further scheme are as follows: the three shafts can be directly braked to prevent power output.
Further, the power input system is provided with a first shaft, a first gear driving gear and a second gear driving gear, the first shaft is parallel to the second shaft, two ends of the first shaft are rotationally connected with the shell, the first gear driving gear and the second gear driving gear are fixedly connected with the first shaft in a coaxial mode, the first gear driving gear is meshed with the first gear driven gear, and the second gear driving gear is meshed with the second gear driven gear.
The beneficial effects of adopting the further scheme are as follows: the first gear driving gear and the first gear driven gear are always meshed with the second gear driving gear and the second gear driven gear, and the power is transmitted and output through the first gear driving gear or the second gear driving gear.
Drawings
FIG. 1 is a schematic diagram of an embodiment of the present invention;
FIG. 2 is a second schematic diagram of an embodiment of the present invention;
FIG. 3 is a schematic illustration of an embodiment of the present invention in neutral;
FIG. 4 is a schematic diagram of a first gear according to an embodiment of the present invention;
FIG. 5 is a schematic diagram of a second gear according to an embodiment of the present invention;
FIG. 6 is a schematic illustration of a first cylinder and first piston assembly connection according to an embodiment of the present invention;
in the figure: 1-housing, 2-motor, 21-coupling sleeve, 3-first shaft, 31-first gear drive gear, 32-second gear drive gear, 4-second shaft, 41-first gear driven gear, 42-gear hub, 43-second gear driven gear, 44-second gear normally engaged gear, 45-slipping engagement transmission, 46-coupling gear, 5-three shaft, 51-three shaft normally engaged gear, 52-three shaft final gear, 6-differential, input gear of 61-differential, 62-first output shaft, 63-second output shaft, 71-first brake, 72-second brake, 73-third brake, 81-first cylinder, 811-first oil inlet, 812-first motor connection port, 813-first oil return hole, 814-first adjusting bolt 815-first oil chamber, 816-first yoke bore, 817-first adjustment threaded bore, 82-second cylinder, 821-second oil inlet, 822-second motor connection port, 823-second oil return bore, 824-second adjustment bolt, 825-second oil chamber, 826-second yoke bore, 827-second adjustment threaded bore, 83-first piston assembly, 831-first valve spool, 8311-first valve spool slot, 832-first piston, 8321-first piston bore, 84-second piston assembly, 841-second valve spool, 8411-second valve spool slot, 842-second piston, 8421-second piston bore, 85-yoke, 86-yoke, 87-locking ball, 881-first guide positioning sleeve, 8811-a first positioning sleeve oil return hole, 882-a second guiding positioning sleeve, 8821-a second positioning sleeve oil return hole and 89-a steel wire retainer ring.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings, in order to make the objects, technical solutions and advantages of the present invention more apparent.
As shown in fig. 1 to 6, the electro-hydraulic control gear shifting gearbox disclosed by the invention comprises a hydraulic gear shifting system, a shell 1, a power input system, a power output system, a two-shaft 4, a first-gear driven gear 41, a second-gear driven gear 43, a gear hub 42, a sliding meshing transmission piece 45 and a two-shaft normal gear 44, wherein the power input system comprises a motor 2, a first shaft 3, a first-gear driving gear 31 and a second-gear driving gear 32, the power output system comprises a three-shaft 5 and a three-shaft normal gear 51, the first shaft 3, the two-shaft 4 and the three-shaft 5 are arranged in parallel in the shell 1, two ends of the first shaft 3, the two-shaft 4 and the three-shaft 5 are rotationally connected with the shell 1 through bearings, one end of the first shaft 3 is connected with an output shaft of the motor 2 through a spline coupling sleeve 21, the motor 2 is preferably a hydraulic motor, the first shaft 3 serves as an input shaft of the gearbox, the first gear driving gear 31 and the second gear driving gear 32 are sequentially arranged on the first shaft 3 along the axial direction, the first gear driving gear 31 and the second gear driving gear 32 are coaxially and fixedly connected with the first shaft 3, the first gear driving gear 31 and the second gear driving gear 32 can be connected with the first shaft 3 through splines, the first gear driving gear 31 and the second gear driving gear 32 can also be rigidly connected with the first shaft 3, preferably through splines, the second shaft 4 is sequentially provided with a first driven gear 41, a gear hub 42, a second driven gear 43 and a second shaft normal gear 44 along the axial direction, the first driven gear 41 and the second driven gear 43 are idler gears, the gear hub 42 is connected with the second shaft 4 through spline transmission, the second shaft normal gear 44 is coaxially and fixedly connected with the second shaft 4, preferably rigidly connected, the third shaft normal gear 51 is coaxially and fixedly connected with the third shaft 5, preferably rigidly connected, the first driven gear 41 is meshed with the first gear driving gear 31, the second-gear driven gear 43 is meshed with the second-gear driving gear 32, the two-axis normal-engaged gear 44 is meshed with the three-axis normal-engaged gear 51, the hydraulic gear shifting system is fixedly connected with the shell 1, the sliding engagement transmission member 45 is meshed with the gear hub 42, and the end portions, close to the gear hub 42, of the first-gear driven gear 41 and the second-gear driven gear 43 are provided with combining teeth 46 matched with the sliding engagement transmission member 45.
The slip engagement transmission 45 is used to transmit the power of the first-gear driven gear 41 or the second-gear driven gear 43 to the gear hub 42 or disconnect the transmission connection of the first-gear driven gear 41 and the second-gear driven gear 43 with the gear hub 42.
The hydraulic gear shifting system is used for driving the sliding engagement transmission member 45 to axially reciprocate along the two shafts 4 so that the sliding engagement transmission member 45 is only engaged with the gear hub 42 and is in neutral gear; or the slip engagement transmission member 45 is simultaneously engaged with the hub 42 and the engaging teeth 46 of the first-gear driven gear 41, which is first-gear at this time; or the slip engagement transmission 45 is simultaneously engaged with the hub 42 and the engaging teeth 46 of the second-gear driven gear 43, which is the second gear.
The triaxial 5 is used for power take-off, and the slipping engagement transmission member 45 can be an engagement sleeve or a slipping gear.
When the motor 2 outputs power, the motor 2 drives the first shaft 3 to rotate, the first shaft 3 drives the first gear driving gear 31 and the second gear driving gear 32 on the first shaft 3 to rotate, the first gear driving gear 31 and the second gear driving gear 32 respectively transmit power to the first gear driven gear 41 and the second gear driven gear 43, when the first gear driving gear and the second gear driving gear are in a neutral state, the sliding engagement transmission piece 45 is only meshed with the gear hub 42, as the first gear driven gear 41 and the second gear driven gear 43 are free gears, when the sliding engagement transmission piece 45 is not meshed with the first gear driven gear 41 or the second gear driven gear 43, the second shaft 4 does not have power input, when the sliding engagement transmission piece 45 is not meshed with the first gear driven gear 41 or the second gear driven gear 43, the motor 2 stops inputting power, the hydraulic gear shifting system drives the sliding engagement transmission piece 45 to move along the axial direction of the second shaft 4 to drive the sliding engagement transmission piece 45 to move forwards and backwards along the axial direction of the second shaft 4, when the sliding engagement transmission piece 45 is meshed with the first gear driven gear 41 and the gear hub 42, after the gear shifting is completed, the power of the first gear driven gear 41 is transmitted to the gear hub 42 through the sliding engagement transmission piece 45, the gear hub 42 is connected with the second shaft 4 through the gear hub 4, and the gear hub 4 is rotated to the constant shaft 5, and the gear shaft is rotated according to the constant speed 51; when the sliding engagement transmission piece 45 is engaged with the second-gear driven gear 43 and the gear hub 42 at the same time, the second-gear shifting is completed, the motor 2 is started after the gear shifting is completed, the power of the second-gear driven gear 43 is transmitted to the gear hub 42 through the sliding engagement transmission piece 45, the gear hub 42 drives the two shafts 4 to rotate, the power is transmitted to the three shafts 5 through the two shaft normally-engaged gear 44 and the three shaft normally-engaged gear 51 and is output according to the speed of the second gear, the sliding engagement transmission piece 45 is driven to reciprocate through the hydraulic gear shifting system, the operation is simple, the maintenance is convenient, the reliability is high, the direct gear shifting without gear selection process is realized, the gear shifting time is shortened, the power loss in the gear shifting process is reduced, and the power performance, the fuel economy and the driving comfort are improved.
Specifically, the hydraulic gear shifting system includes a first cylinder 81, a second cylinder 82, a first piston assembly 83, a second piston 842 assembly 84, a shifting fork 86 and a fork shaft 85, the first cylinder 81 and the second cylinder 82 are oppositely disposed at two sides of the housing 1, the first piston assembly 83 is slidably disposed in the first cylinder 81 and separates the inner cavity of the first cylinder 81 into a first oil cavity 815 and a first fork shaft cavity 823, the first oil cavity 815 is provided with a first oil inlet 811, the second piston 842 assembly 84 is slidably disposed in the second cylinder 82 and separates the inner cavity of the second cylinder 82 into a second oil cavity 825 and a second fork shaft cavity 826, the second oil cavity 825 is provided with a second oil inlet 821, two ends of the fork shaft 85 are slidably disposed in the first fork shaft cavity 823 and the second fork shaft cavity 826, the end of the fork shaft 85 is in butt joint with the first piston assembly 83, the end of the fork shaft 85 in the second fork shaft cavity 826 is in butt joint with the second piston 842 assembly 84, the fork shaft 85 is in sliding connection with the housing 1 and parallel with the second shaft 4, the second piston 842 is in parallel with the fork 86, the shifting fork 86 is in fixed connection with the second fork shaft 86 and the second fork shaft 86, the second piston 86 is in the second piston assembly 86 is in the limit groove 45, the limit groove is engaged with the second end of the second piston assembly, the second piston assembly is engaged with the second end 45, and the second end of the second piston assembly is engaged with the second end groove, the second end groove is engaged with the limit groove, and the limit groove is engaged with the limit groove 45, the limit groove is engaged with the limit groove.
The first oil inlet 811 is used for injecting hydraulic oil into the first oil cavity 815, so that the first piston assembly 83 can push the fork shaft 85 and the shifting fork 86 to move towards the second cylinder 82, the second oil inlet 821 is used for injecting hydraulic oil into the second oil cavity, and the second piston 842 assembly 84 can push the fork shaft 85 and the shifting fork 86 to move towards the second cylinder 82, so that the shifting fork 86 drives the sliding engagement transmission member 45 to axially reciprocate along the two shafts 4, and gear shifting is realized.
As a further solution of this embodiment, a first motor connection port 812 is opened in the middle of the first cylinder 81, a second motor connection port 822 is opened in the middle of the second cylinder 82, both the first motor connection port 812 and the second motor connection port 822 are communicated with the hydraulic motor 2, the first piston assembly 83 has a first piston oil passage, the second piston 842 assembly 84 has a second piston oil passage, when the sliding engagement transmission member 45 is in contact with the end of the coupling tooth 46 of the first gear driven gear 41, the second oil chamber 825 is communicated with the second motor connection port 822 through the second piston oil passage, and when the sliding engagement transmission member 45 is in contact with the end of the coupling tooth 46 of the second gear driven gear 43, the first oil chamber 815 is communicated with the first motor connection port 812 through the first piston oil passage.
During gear shifting, the hydraulic motor 2 stops power input, before gear shifting is completed, part of hydraulic oil flows into the hydraulic motor 2 through the first motor connecting port 812 or the second motor connecting port 822, the hydraulic motor 2 is driven to drive the first shaft 3 to rotate by a certain angle, so that the sliding engagement transmission piece 45 can smoothly cut into the combination teeth 46 of the first gear driven gear 41 or the second gear driven gear 43 and is engaged with the first gear driven gear 41 or the second gear driven gear 43, the phenomenon that the sliding engagement transmission piece 45 and the first gear driven gear 41 or the second gear driven gear 43 are in a tooth-to-tooth mode in the moving process of the sliding engagement transmission piece 45 is avoided, engagement cannot be completed, and the phenomenon that gear is not hung up is avoided.
Specifically, the first piston assembly 83 includes a first piston 832 and a first valve element 831, the first piston 832 is slidably disposed in the first cylinder 81, and the inner cavity of the first cylinder 81 is a first oil cavity 815 and a first fork shaft cavity 823, the first piston 832 has a first valve element mounting hole penetrating through both ends of the moving direction and adapted to the first valve element 831, the first valve element 831 is mounted in the first valve element mounting hole, the first piston 832 has a first piston hole 8321, the first valve element 831 has a first valve element groove 8311, during the second gear, the sliding engagement transmission member 45 contacts with the end of the engaging tooth 46 of the second driven gear 43, the first piston hole 8321 communicates with the first motor connection port 812 and the first valve element groove 8311 communicates with the first oil cavity 815, and the first valve element groove 8311 communicates with the first piston hole 8321 to form a first piston oil duct; the second piston 842 assembly 84 includes a second piston 842 and a second spool 841, the second piston 842 being slidably disposed within the second cylinder 82 and having a second oil chamber 825 and a second spool chamber 826 in the second cylinder 82, the second piston 842 having a second spool mounting hole extending through both ends in the direction of movement and adapted to the second spool 841, the second spool 841 being mounted in the second spool mounting hole, the second piston 842 having a second piston hole 8421, the second spool 841 having a second spool groove 8411, the sliding engagement transmission 45 being in contact with an end of the first driven gear 41 engaging tooth 46 during a first gear, the second piston hole 8421 being in communication with the second motor connecting port 822 and the second spool groove 8411 being in communication with the second oil chamber 825, the second spool groove 8411 being in communication with the second piston hole 8421 to form a second piston oil passage.
Before the sliding engagement transmission piece 45 reaches the end part of the first-gear driven gear 41 or the second-gear driven gear 43, hydraulic oil in the hydraulic gear shifting system cannot enter the hydraulic motor 2, the first piston oil duct and the second piston oil duct are blocked, hydraulic oil leakage in the first oil cavity 815 and the second oil cavity 825 is reduced, enough thrust is kept in the first oil cavity 815 or the second oil cavity 825 to push the fork shaft 85 and the fork 86 to move, and the fork 86 drives the sliding engagement transmission piece 45 to reach the end part position of the first-gear driven gear 41 or the second-gear driven gear 43, and the first piston oil duct or the second piston oil duct is communicated with the hydraulic motor 2, so that hydraulic oil enters the hydraulic motor 2 and drives the first shaft 3 to rotate for a certain angle.
As a further scheme of this embodiment, the hydraulic control valve further includes a first guiding and positioning sleeve 881 and a second guiding and positioning sleeve 882, the first guiding and positioning sleeve 881 is fixed at one end of the first cylinder 81 close to the inner cavity of the housing 1, the second guiding and positioning sleeve 882 is fixed at one end of the second cylinder 82 close to the inner cavity of the housing 1, the fork shaft 85 is slidably disposed in the first guiding and positioning sleeve 881 and the second guiding and positioning sleeve 882, the first valve spool 831 is slidably disposed in the first valve spool mounting hole, and the second valve spool 841 is slidably disposed in the second valve spool mounting hole.
When the second gear is engaged, the first piston assembly 83 pushes the fork shaft 85 to enable the sliding engagement transmission member 45 to be in contact with the end portion of the combining tooth 46 of the second gear driven gear 43, the end portion of the first piston 832 is in abutting contact with the first guiding and positioning sleeve 881, the first valve element 831 continues to push the fork shaft 85 to move to enable the sliding engagement transmission member 45 to be in engagement with the combining tooth 46 of the second gear driven gear 43, and the first valve element groove 8311 is disconnected from the first oil cavity 815.
In first gear, the second piston 842 assembly 84 pushes the fork shaft 85 to bring the slidably engaged transmission 45 into contact with the end of the engaging teeth 46 of the first-gear driven gear 41, the end of the second piston 842 abuts the second guide positioning sleeve 882, the second spool 841 continues to push the fork shaft 85 to move to engage the slidably engaged transmission 45 with the engaging teeth 46 of the first-gear driven gear 41, and the second spool groove 8411 is disconnected from the second oil chamber 825.
When the first piston 832 moves to be in contact with the first guide positioning sleeve 881, the first piston oil duct is communicated with the first oil cavity 815 and the first motor connecting port 812, the first valve element 831 continues to move to finish gear shifting, and after the first valve element 831 moves, the first valve element groove 8311 is disconnected from the first oil cavity 815 and no oil is fed into the hydraulic motor 2; or the second valve element 841 slides in the second piston 842, when the second piston 842 moves to be in contact with the second guiding positioning sleeve 882, the second piston oil duct communicates the second oil cavity 825 with the second motor connecting port 822, the second valve element 841 continues to move to finish gear shifting, and after the second valve element 841 moves, the second valve element groove 8411 is disconnected from the second oil cavity 825, and no oil is fed into the hydraulic motor 2.
As a further solution of this embodiment, both ends of the first spool 831 and the second spool 841 are sleeved with a wire retainer ring 89, and the wire retainer ring 89 is used for limiting the first spool 831 or the second spool 841 connected with the wire retainer ring. Specifically, annular retainer grooves are machined on the outer walls of the two ends of the first valve element 831 and the second valve element 841, and steel wire retainer rings 89 are embedded in the retainer grooves in a one-to-one correspondence mode.
As a further aspect of the present embodiment, the first fork shaft chamber 823 and the second fork shaft chamber 826 are respectively opened with a first oil return hole 813 and a second oil return hole 823, the first oil return hole 813 and the second oil return hole 823 are both communicated with a hydraulic oil tank for storing hydraulic oil, a gap is provided between the first valve spool 831 and the first piston 832, a gap is provided between the second valve spool 841 and the second piston 842, a gap is provided between the fork shaft 85 and the first guide positioning sleeve 881 and the second guide positioning sleeve 882, the first guide positioning sleeve 881 is opened with a first positioning sleeve oil return hole 8811 which is communicated with the first oil return hole 813, the second guide positioning sleeve 882 is opened with a second positioning sleeve oil return hole 8821 which is communicated with the second oil return hole 823, a gap between the first valve spool 831 and the first piston 832 is communicated with a gap between the fork shaft 85 and the first guide positioning sleeve 881, a gap between the second valve spool 882 and the second piston 842 is communicated with a gap between the fork shaft 85 and the second guide positioning sleeve 882, and a gap between the fork shaft 85 and the second positioning sleeve 881 is communicated with the second positioning sleeve oil return hole 88 and the second positioning sleeve oil return hole 8821.
Specifically, the first positioning sleeve oil return hole 8811 is disposed along the radial direction of the first guiding positioning sleeve 881, one end of which is communicated with the first positioning sleeve oil return hole 8811, and the other end of which is communicated with the gap between the first positioning sleeve and the fork shaft 85. The outer side of the first guide positioning sleeve 881 corresponding to one end of the first positioning sleeve oil return hole 8811 is also provided with an annular first oil return groove which is communicated with one end of the first positioning sleeve oil return hole 8811; the second positioning sleeve oil return hole 8821 is disposed along the radial direction of the second guiding positioning sleeve 882, and has one end communicating with the second positioning sleeve oil return hole 8821 and the other end communicating with the gap between the second positioning sleeve and the fork shaft 85. The outer side of the second guide sleeve 882 corresponding to one end of the second positioning sleeve oil return hole 8821 is further provided with an annular second oil return groove, and the second oil return groove is communicated with one end of the second positioning sleeve oil return hole 8821.
As a further scheme of this embodiment, the inner side of one end of the first guiding and positioning sleeve 881 and the second guiding and positioning sleeve 882, which is close to the inner cavity of the housing 1, is provided with a positioning sleeve inner sealing groove, and the inner sealing grooves of the positioning sleeves of the first guiding and positioning sleeve 881 and the second guiding and positioning sleeve 882 are embedded with the fork shaft sealing ring.
As a further scheme of the embodiment, the hydraulic cylinder further comprises a first adjusting bolt 814 and a second adjusting bolt 824, wherein one end of the first cylinder 81 is provided with a first adjusting threaded hole 817 coaxially arranged with the first piston assembly 83, the first adjusting bolt 814 is in threaded connection with the first adjusting threaded hole 817, and one end of the first adjusting bolt 814 extends into the first oil cavity 815; one end of the second cylinder 82 has a second adjustment threaded hole 827 coaxially disposed with the second piston 842 assembly 84, the second adjustment bolt 824 is threadedly coupled to the second adjustment threaded hole 827, and one end thereof extends into the second oil chamber 825, and the first adjustment bolt 814 and the second adjustment bolt 824 can limit the position of the fork shaft 85 to move to both sides.
As a further scheme of the embodiment, the hydraulic cylinder further comprises a first sealing nut and a second sealing nut, wherein the first sealing nut and the first adjusting threaded hole 817 are coaxially arranged and fixedly connected to the outer side of the first cylinder 81, and the first adjusting bolt 814 is in threaded connection with the first sealing nut; the second sealing nut is coaxially disposed with the second adjusting screw hole 827 and fixedly coupled to the outer side of the second cylinder 82, and the second adjusting bolt 824 is screw-coupled with the second sealing nut.
As a further solution of this embodiment, the piston sealing device further includes a first sealing ring, the outer walls of the first piston 832 and the second piston 842 have annular piston sealing grooves, the piston sealing grooves are located between the first piston hole 8321 or the second piston hole 8421 and the fork shaft 85, the first sealing rings are embedded in the piston sealing grooves of the first piston 832 and the second piston 842, and the first sealing rings seal the gaps between the first piston 832 and the first cylinder 81 and between the second piston 842 and the second cylinder 82, so as to avoid oil leakage.
As a further scheme of this embodiment, still include the second sealing washer, the opening edge department that first cylinder body 81 and second cylinder body 82 are close to the inner chamber of casing 1 all is equipped with the cylinder body seal groove, and the cylinder body seal groove of first cylinder body 81 and second cylinder body 82 is embedded to be equipped with the second sealing washer in.
As a further scheme of this embodiment, the outer side walls of the first guiding locating sleeve 881 and the second guiding locating sleeve 882, which are close to one end of the inner cavity of the housing 1, are respectively provided with a locating sleeve outer sealing groove, and the locating sleeve outer sealing grooves of the first guiding locating sleeve 881 and the second guiding locating sleeve 882 are respectively embedded with a third sealing ring.
As a further scheme of this embodiment, still include locking ball 87, the upside outer wall of fork shaft 85 has opened first locking hole, second locking hole and third locking hole along the axial in proper order, casing 1 and fork shaft 85 sliding connection part separate have the locking passageway that supplies locking ball 87 to remove, locking passageway upper end seals and lower extreme opening, the locking passageway is vertical, locking ball 87 elasticity spacing is in the locking passageway, the locking ball 87 top is provided with hold-down spring, hold-down spring both ends respectively with locking ball 87 and locking passageway upper end butt, through first locking hole or second locking hole or third locking hole and locking ball 87 and locking passageway cooperation, with fork shaft 85 in corresponding position auto-lock, prevent that it from moving by oneself along the axial, specifically:
When the second gear is engaged, the sliding engagement transmission piece 45 is simultaneously engaged with the gear hub 42 and the combination gear 46 of the second gear driven gear 43, the lower end of the locking channel is opposite to the first locking hole, the lower part of the locking ball 87 is embedded into the first locking hole, and the upper part of the locking ball 87 is arranged in the locking channel;
when the gear is engaged in the neutral gear, the sliding engagement transmission piece 45 is only engaged with the gear hub 42, the lower end of the locking channel is opposite to the second locking hole, the lower part of the locking ball 87 is embedded into the second locking hole, and the upper part of the locking ball 87 is arranged in the locking channel;
when a first gear is engaged, the sliding engagement transmission member 45 is simultaneously engaged with the gear hub 42 and the engaging teeth 46 of the first-gear driven gear 41, the lower end of the locking passage is opposite to the third locking hole, the lower part of the locking ball 87 is embedded into the third locking hole, and the upper part of the locking ball 87 is arranged in the locking passage.
After the shift is completed, the lower portion of the locking balls 87 is inserted into the corresponding locking holes and engaged with the locking passages to prevent the fork shaft 85 from moving, and the slip engagement transmission member 45 is kept engaged with the corresponding parts, thereby preventing the fork shaft 85 from moving randomly in the non-shift state.
As a further scheme of the embodiment, the three-shaft final drive device further comprises a differential mechanism 6 and a three-shaft final drive gear 52, wherein the three-shaft final drive gear 52 is arranged on the three shafts 5 and is fixedly connected with the three shafts 5 coaxially, the three-shaft final drive gear 52 is meshed with an input gear 61 of the differential mechanism, and power input by the motor 2 is output through the differential mechanism 6 through the three shafts 5.
As a further solution of the present embodiment, the differential 6 has a first output shaft 62 and a second output shaft 63, the first output shaft 62 and the second output shaft 63 are respectively rotatably connected to two opposite sides of the housing 1, the first brake 71 and the second brake 72 are respectively disposed on two opposite sides of the housing 1, the first brake 71 is used for braking the first output shaft 62, the second brake 72 is used for braking the second output shaft 63, the third brake 73 is disposed at one end of the triaxial 5 on the housing 1, the third brake 73 is used for braking the triaxial 5, the third brake 73 is a hand brake, and the method of connecting the brake with the housing 1 for braking the spindle is the prior art.
Of course, the present invention is capable of other various embodiments and its several details are capable of modification and variation in light of the present invention by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (9)
1. An electrohydraulic control gear shift gearbox, characterized in that: the hydraulic gear shifting device comprises a hydraulic gear shifting system, a shell (1), a power input system, a two-shaft (4), a sliding engagement transmission piece (45) and a power output system, wherein two ends of the two-shaft (4) are rotationally connected with the shell (1), a first-gear driven gear (41), a gear hub (42) and a second-gear driven gear (43) are sequentially arranged on the two-shaft (4) along the axial direction of the two-shaft, the first-gear driven gear (41) and the second-gear driven gear (43) are idler gears, the gear hub (42) is in transmission connection with the two-shaft (4), the first-gear driven gear (41) and the second-gear driven gear (43) are in transmission connection with the power input system, the two-shaft is in transmission connection with the power output system, the hydraulic gear shifting system is fixedly connected with the shell (1), and the sliding engagement transmission piece (45) is meshed with the gear hub (42).
The hydraulic gear shifting system is used for driving the sliding engagement transmission member (45) to axially reciprocate along the two shafts (4) so that the sliding engagement transmission member (45) is only engaged with the gear hub (42) to realize neutral gear, or the sliding engagement transmission member (45) is simultaneously engaged with the gear hub (42) and the first-gear driven gear (41) to realize first gear, or the sliding engagement transmission member (45) is simultaneously engaged with the gear hub (42) and the second-gear driven gear (43) to realize second gear;
the hydraulic gear shifting system comprises a first cylinder body (81), a second cylinder body (82), a first piston assembly (83), a second piston assembly (84), a shifting fork (86) and a fork shaft (85), wherein the first cylinder body (81) and the second cylinder body (82) are oppositely arranged on two sides of the shell (1), the first piston assembly (83) is slidably arranged in the first cylinder body (81) and divides the inner cavity of the first cylinder body (81) into a first oil cavity (815) and a first fork shaft cavity (816), the first oil cavity (815) is provided with a first oil inlet (811), the second piston assembly (84) is slidably arranged in the second cylinder body (82) and divides the inner cavity of the second cylinder body (82) into a second oil cavity (825) and a second fork shaft cavity (826), two ends of the fork shaft (85) are slidably arranged in the first fork shaft cavity (816) and the second fork shaft cavity (816) respectively, the second piston assembly (826) is abutted against the end part of the second piston assembly (85) in the second fork shaft cavity (85), the fork shaft (85) is in sliding connection with the shell (1) and is parallel to the two shafts (4), the shifting fork (86) is fixedly connected with the fork shaft (85), and the shifting fork (86) is arranged in the shell and is used for driving the sliding engagement transmission piece (45) to axially reciprocate along the two shafts (4);
A first motor connecting port (812) is formed in the middle of the first cylinder body (81), a second motor connecting port (822) is formed in the middle of the second cylinder body (82), the first piston assembly (83) is provided with a first piston oil duct, and the second piston assembly (84) is provided with a second piston oil duct;
when a first gear is engaged, the second oil cavity (825) is communicated with the second motor connecting port (822) through the second piston oil duct; when a second gear is engaged, the first oil cavity (815) is communicated with the first motor connection port (812) through the first piston oil duct;
the first piston assembly (83) comprises a first piston (832) and a first valve core (831), the first piston (832) is slidably arranged in the first cylinder body (81), the inner cavity of the first cylinder body (81) is divided into a first oil cavity (815) and a first fork shaft cavity (816), the first piston (832) is provided with a first valve core mounting hole penetrating through two ends of the moving direction of the first piston (832), the first piston (832) is provided with a first piston assembly hole (8321), the first valve core (831) is provided with a first valve core groove (8311), and when in gear shifting, the first piston assembly hole (8321) is communicated with the first motor connecting port (812) and the first valve core groove (8311) is communicated with the first oil cavity (815), and the first valve core groove (8311) is communicated with the first piston assembly hole (8321) to form the first oil duct.
2. The electro-hydraulically controlled shift gearbox of claim 1, wherein: the power input system is provided with a hydraulic motor (2), the output end of the hydraulic motor (2) is in transmission connection with the first-gear driven gear (41) and the second-gear driven gear (43), and the first motor connecting port (812) and the second motor connecting port (822) are communicated with the hydraulic motor (2).
3. The electro-hydraulically controlled shift gearbox of claim 1, wherein: the second piston assembly (84) comprises a second piston (842) and a second valve core (841), the second piston (842) is slidably arranged in the second cylinder body (82) and divides the inner cavity of the second cylinder body (82) into a second oil cavity (825) and a second branch shaft cavity (826), the second piston (842) is provided with a second valve core mounting hole penetrating through two ends of the second piston assembly in the moving direction, the first valve core (831) is penetrated in the first valve core mounting hole, the second piston (842) is provided with a second piston hole (8421), the second valve core (841) is provided with a second valve core groove (8411), when a gear is engaged, the second piston hole (8421) is communicated with the second motor connecting port (822) and the second valve core groove (8411) is communicated with the second oil cavity (825), and the second valve core groove (8411) is communicated with the second piston hole (8421) to form the second oil duct.
4. An electro-hydraulically controlled shift gearbox as claimed in claim 3, wherein: the hydraulic control valve further comprises a first guide positioning sleeve (881) and a second guide positioning sleeve (882), wherein the first guide positioning sleeve (881) is fixed at one end, close to the inner cavity of the shell (1), in the first cylinder body (81), the second guide positioning sleeve (882) is fixed at one end, close to the inner cavity of the shell (1), in the second cylinder body (82), the fork shaft (85) is slidably arranged in the first guide positioning sleeve (881) and the second guide positioning sleeve (882), the first valve core (831) is slidably arranged in the first valve core mounting hole, and the second valve core (841) is slidably arranged in the second valve core mounting hole;
when a second gear is engaged, the end part of the first piston (832) is abutted against the first guiding locating sleeve (881), the first valve core (831) continuously pushes the fork shaft (85) to move so that the sliding engagement transmission member (45) is engaged with the second gear driven gear (43), and the first valve core groove (8311) is disconnected with the first oil cavity (815);
when a first gear is engaged, the end part of the second piston (842) is abutted with the second guiding locating sleeve (882), the second valve core (841) continuously pushes the fork shaft (85) to move so that the sliding engagement transmission member (45) is engaged with the first gear driven gear (41), and the second valve core groove (8411) is disconnected with the second oil cavity (825).
5. The electro-hydraulically controlled shift gearbox of claim 1, wherein: the locking device comprises a fork shaft (85), and is characterized by further comprising a locking ball (87), wherein a first locking hole, a second locking hole and a third locking hole are sequentially formed in the outer wall of the fork shaft (85) along the axial direction, a locking channel for the locking ball (87) to move is formed in the sliding connection part of the shell (1) and the fork shaft (85), the lower end of the locking channel is opened, and the locking ball (87) is elastically limited in the locking channel;
when the second gear is engaged, the lower end of the locking channel is opposite to the first locking hole, the lower part of the locking ball (87) is embedded into the first locking hole, and the upper part of the locking ball (87) is arranged in the locking channel;
when the gear is engaged, the lower end of the locking channel is opposite to the second locking hole, the lower part of the locking ball (87) is embedded into the second locking hole, and the upper part of the locking ball (87) is arranged in the locking channel;
when a first gear is engaged, the lower end of the locking channel is opposite to the third locking hole, the lower part of the locking ball (87) is embedded into the third locking hole, and the upper part of the locking ball (87) is arranged in the locking channel.
6. The electro-hydraulically controlled shift gearbox of any one of claims 1-5, wherein: the power output system comprises a triaxial (5), a triaxial final drive gear (51), a triaxial final drive gear (52) and a differential mechanism (6), wherein the triaxial (5) is parallel to the biaxial (4) and both ends of the triaxial final drive gear are rotationally connected with the shell (1), the triaxial final drive gear (51) and the triaxial final drive gear (52) are fixedly connected with the triaxial (5), the biaxial (4) is further coaxially and fixedly connected with a biaxial final drive gear (44), the triaxial final drive gear (51) is meshed with the biaxial final drive gear (44), the triaxial final drive gear (52) is meshed with an input gear (61) of the differential mechanism, and power input by the power input system is output through the differential mechanism (6).
7. The electro-hydraulically controlled shift gearbox of claim 6, wherein: still include first stopper (71) and second stopper (72), differential mechanism (6) have first output shaft (62) and second output shaft (63), first output shaft (62) with second output shaft (63) respectively with the both sides rotation that casing (1) is relative are connected, first stopper (71) with second stopper (72) set up respectively in casing (1) is relative both sides, first stopper (71) are used for the braking first output shaft (62), second stopper (72) are used for the braking second output shaft (63).
8. The electro-hydraulically controlled shift gearbox of claim 6, wherein: the three-shaft brake device further comprises a third brake (73), wherein the third brake (73) is arranged at one end of the three shafts (5) on the shell (1), and the third brake (73) is used for braking the three shafts (5).
9. The electro-hydraulically controlled shift gearbox of any one of claims 1-5, wherein: the power input system is provided with a first shaft (3), a first gear driving gear (31) and a second gear driving gear (32), wherein the first shaft (3) is parallel to the second shaft (4) and both ends of the first shaft are rotationally connected with the shell (1), the first gear driving gear (31) and the second gear driving gear (32) are fixedly connected with the first shaft (3) coaxially, the first gear driving gear (31) is meshed with the first gear driven gear (41), and the second gear driving gear (32) is meshed with the second gear driven gear (43).
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| CN201910832159.2A CN110469649B (en) | 2019-09-04 | 2019-09-04 | Electrohydraulic control gear shifting gearbox |
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| CN201910832159.2A CN110469649B (en) | 2019-09-04 | 2019-09-04 | Electrohydraulic control gear shifting gearbox |
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Citations (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003120808A (en) * | 2001-10-18 | 2003-04-23 | Fuji Heavy Ind Ltd | Automatic transmission |
| JP2004060752A (en) * | 2002-07-29 | 2004-02-26 | Fuji Heavy Ind Ltd | Gear change mechanism of transmission for vehicle |
| CN2826091Y (en) * | 2005-05-13 | 2006-10-11 | 六安江淮汽车齿轮制造有限公司 | Automobile transmission |
| JP2007107621A (en) * | 2005-10-14 | 2007-04-26 | Nissan Motor Co Ltd | Shift actuator drive control device for automatic manual transmission |
| JP2008114674A (en) * | 2006-11-02 | 2008-05-22 | Univance Corp | Driving force distribution device for four-wheel drive vehicle |
| CN101245850A (en) * | 2008-03-20 | 2008-08-20 | 重庆大学 | Mechanical automatic speed-changing direct-shifting hydraulic actuator of heavy vehicle |
| CN101435503A (en) * | 2008-12-19 | 2009-05-20 | 长沙航空工业中南传动机械厂 | Electromagnetic valve controlled pneumatic shift automatic speed variator |
| CN101498352A (en) * | 2008-12-16 | 2009-08-05 | 赣州五环机器有限责任公司 | Forklift speed variator |
| EP2251569A1 (en) * | 2009-05-12 | 2010-11-17 | Toyota Jidosha Kabushiki Kaisha | Shift hydraulic actuator |
| CN102398471A (en) * | 2011-07-19 | 2012-04-04 | 山东临沂临工汽车桥箱有限公司 | Driving axle for harvester with high feeding capacity |
| CN103703287A (en) * | 2011-05-25 | 2014-04-02 | 技术推进公司 | Device for translatably controlling movement of gear change fork for motor vehicle gearbox |
| EP2843267A1 (en) * | 2013-08-08 | 2015-03-04 | Linde Hydraulics GmbH & Co. KG | Hydraulic shift actuator of a mechanical two gear transmission |
| CN104455240A (en) * | 2014-12-01 | 2015-03-25 | 重庆先友科技开发有限公司 | Synchronous two-stage transmission for vehicle |
| CN104633097A (en) * | 2013-11-08 | 2015-05-20 | 本田技研工业株式会社 | Shift actuator |
| CN106641224A (en) * | 2017-01-22 | 2017-05-10 | 山东海卓电液控制工程技术研究院 | AMT hydraulic gear-shifting execution system having mechanical centering function |
| CN107061665A (en) * | 2017-03-27 | 2017-08-18 | 山东卫禾传动科技有限公司 | A kind of reversely input agricultural equipment gearbox |
| JP2018076907A (en) * | 2016-11-09 | 2018-05-17 | 本田技研工業株式会社 | Shift piston device |
| CN207470762U (en) * | 2017-07-18 | 2018-06-08 | 重庆福特来动力科技有限公司 | Electric vehicle automatic gear shift apparatus |
| CN208169440U (en) * | 2018-02-09 | 2018-11-30 | 温岭市明华齿轮有限公司 | Double dynamical chang-over speed reducing box |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005011273A1 (en) * | 2005-03-11 | 2006-09-21 | Zf Friedrichshafen Ag | Method for controlling shift sequences in an automatic gearbox in countershaft design |
-
2019
- 2019-09-04 CN CN201910832159.2A patent/CN110469649B/en active Active
Patent Citations (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003120808A (en) * | 2001-10-18 | 2003-04-23 | Fuji Heavy Ind Ltd | Automatic transmission |
| JP2004060752A (en) * | 2002-07-29 | 2004-02-26 | Fuji Heavy Ind Ltd | Gear change mechanism of transmission for vehicle |
| CN2826091Y (en) * | 2005-05-13 | 2006-10-11 | 六安江淮汽车齿轮制造有限公司 | Automobile transmission |
| JP2007107621A (en) * | 2005-10-14 | 2007-04-26 | Nissan Motor Co Ltd | Shift actuator drive control device for automatic manual transmission |
| JP2008114674A (en) * | 2006-11-02 | 2008-05-22 | Univance Corp | Driving force distribution device for four-wheel drive vehicle |
| CN101245850A (en) * | 2008-03-20 | 2008-08-20 | 重庆大学 | Mechanical automatic speed-changing direct-shifting hydraulic actuator of heavy vehicle |
| CN101498352A (en) * | 2008-12-16 | 2009-08-05 | 赣州五环机器有限责任公司 | Forklift speed variator |
| CN101435503A (en) * | 2008-12-19 | 2009-05-20 | 长沙航空工业中南传动机械厂 | Electromagnetic valve controlled pneumatic shift automatic speed variator |
| EP2251569A1 (en) * | 2009-05-12 | 2010-11-17 | Toyota Jidosha Kabushiki Kaisha | Shift hydraulic actuator |
| CN103703287A (en) * | 2011-05-25 | 2014-04-02 | 技术推进公司 | Device for translatably controlling movement of gear change fork for motor vehicle gearbox |
| CN102398471A (en) * | 2011-07-19 | 2012-04-04 | 山东临沂临工汽车桥箱有限公司 | Driving axle for harvester with high feeding capacity |
| EP2843267A1 (en) * | 2013-08-08 | 2015-03-04 | Linde Hydraulics GmbH & Co. KG | Hydraulic shift actuator of a mechanical two gear transmission |
| CN104633097A (en) * | 2013-11-08 | 2015-05-20 | 本田技研工业株式会社 | Shift actuator |
| CN104455240A (en) * | 2014-12-01 | 2015-03-25 | 重庆先友科技开发有限公司 | Synchronous two-stage transmission for vehicle |
| JP2018076907A (en) * | 2016-11-09 | 2018-05-17 | 本田技研工業株式会社 | Shift piston device |
| CN106641224A (en) * | 2017-01-22 | 2017-05-10 | 山东海卓电液控制工程技术研究院 | AMT hydraulic gear-shifting execution system having mechanical centering function |
| CN107061665A (en) * | 2017-03-27 | 2017-08-18 | 山东卫禾传动科技有限公司 | A kind of reversely input agricultural equipment gearbox |
| CN207470762U (en) * | 2017-07-18 | 2018-06-08 | 重庆福特来动力科技有限公司 | Electric vehicle automatic gear shift apparatus |
| CN208169440U (en) * | 2018-02-09 | 2018-11-30 | 温岭市明华齿轮有限公司 | Double dynamical chang-over speed reducing box |
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