CN107435733B - Gear shifting hydraulic control system and gearbox - Google Patents
Gear shifting hydraulic control system and gearbox Download PDFInfo
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- CN107435733B CN107435733B CN201710374126.9A CN201710374126A CN107435733B CN 107435733 B CN107435733 B CN 107435733B CN 201710374126 A CN201710374126 A CN 201710374126A CN 107435733 B CN107435733 B CN 107435733B
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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
- F16H61/02—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
- F16H61/0267—Layout of hydraulic control circuits, e.g. arrangement of valves
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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
- F16H61/04—Smoothing ratio shift
- F16H61/06—Smoothing ratio shift by controlling rate of change of fluid pressure
- F16H61/065—Smoothing ratio shift by controlling rate of change of fluid pressure using fluid control means
- F16H61/068—Smoothing ratio shift by controlling rate of change of fluid pressure using fluid control means using an orifice control valve
Abstract
The invention discloses a gear shifting hydraulic control system, which comprises an oil tank for providing hydraulic oil, a group of gear shifting forks driven by the hydraulic oil, gear shifting slide valves with the same number as the gear shifting forks and electromagnetic valves for controlling each gear shifting slide valve, wherein a gear hydraulic interlocking structure is arranged on the same output shaft; the hydraulic oil in the main oil path is selectively input into a first gear shifting main oil path and a second gear shifting main oil path in a piston cavity of a gear shifting fork respectively; and an oil passage switching spool valve for switching the first shift main oil passage and the second shift main oil passage. The invention has the following beneficial effects: the hydraulic interlocking function with the same output shaft gear is achieved, only one gear is combined on the same output shaft, and damage to the gearbox caused by misoperation of the electromagnetic valve is avoided.
Description
Technical Field
The invention relates to the technical field of automobile gearboxes, in particular to a gear shifting hydraulic control system applied to a wet-type double-clutch gearbox.
Background
The wet type double clutch is characterized in that the double clutch is a large group of multi-plate clutches and a small group of multi-plate clutches which are coaxially arranged together, and the multi-plate clutches are all arranged in a closed oil cavity filled with hydraulic oil. Therefore, the wet clutch structure has better adjusting capacity and can transmit larger torque; meanwhile, hydraulic oil can be used for cooling and lubricating, so that the abrasion is small and the heat dissipation is good. For the above reasons, wet double clutches are widely used in the field of automobile manufacturing.
As shown in chinese patents CN201410588154.7 and CN201510362821.4, in the prior art, a hydraulic control system of a wet dual clutch transmission needs to drive a mechanical oil pump through an engine to draw stored hydraulic oil from an oil tank as an oil source to provide oil pressure. Although the hydraulic control system can realize the work of a wet-type double-clutch gearbox, the problems of large fluctuation of main oil pressure, unstable oil pressure control and the like easily occur in a control mode, and the gearbox controlled by the hydraulic control system is carried behind the whole vehicle, can generate gear shifting impact and pause, and is not beneficial to the driving feeling of a driver. The main reasons for this are: the smoothness of the movement of the gear shifting fork is difficult to control because the fluctuation of main oil pressure can bring impact to a pilot control oil path in the gear shifting hydraulic control system, and because of the impact and the fluctuation of the pilot oil path, a gear shifting slide valve controlled by an electromagnetic valve in the system moves along with the fluctuation of the oil pressure, so that the pressure oil passing through the gear shifting slide valve fluctuates and impacts. In addition, there is no interlocking structure in the existing shift hydraulic control system, and there is a risk that two gears are formed on the same output shaft at the same time.
Disclosure of Invention
The invention aims to overcome the defects in the prior art and provide a stable and safe gear shifting hydraulic control system applied to a wet type double-clutch gearbox.
The purpose of the invention is realized by the following technical scheme:
the utility model provides a gear shift hydraulic control system, includes the oil tank that is used for providing hydraulic oil to and the main oil circuit of exporting hydraulic oil from the oil tank, and pass through a set of gear shift fork of hydraulic oil drive, the gear shift fork is used for selectively forming the gear through corresponding synchronous ware and gear wheel, gear wheel includes seven forward gear gears and a reverse gear wheel, and its odd number gear wheel arranges on same root odd number gear output shaft, and its even number gear wheel and reverse gear wheel arrange on another even number gear output shaft, include:
the gear shifting fork mechanism comprises gear shifting slide valves and electromagnetic valves, wherein the number of the gear shifting slide valves is equal to that of the gear shifting fork mechanisms, and the electromagnetic valves are used for controlling each gear shifting slide valve;
the hydraulic oil in the main oil path is selectively input into a first gear shifting main oil path and a second gear shifting main oil path in a piston cavity of a gear shifting fork respectively;
and an oil passage switching spool valve for switching the first shift main oil passage and the second shift main oil passage.
Preferably, the four gear shifting forks and the four gear shifting slide valves corresponding to the four gear shifting forks are included, every two pairs of the gear shifting slide valves and the gear shifting forks act on the same output shaft, each gear shifting slide valve is provided with an electromagnetic valve for controlling the valve core to move, a pilot end and a spring end, the pilot end is communicated with the oil tank through the corresponding electromagnetic valve, the hydraulic interlocking structure is a hydraulic interlocking oil path arranged between the two gear shifting slide valves acting on the same output shaft, one end of the hydraulic interlocking oil path is communicated with the pilot end of one of the gear shifting slide valves, and the other end of the hydraulic interlocking oil path is communicated with the spring end of the other gear shifting slide valve.
Preferably, the main oil path is further provided with a branch which is a pilot oil path, hydraulic oil in the main oil path enters the pilot oil path through a pilot oil pressure control slide valve, the pilot oil pressure control slide valve adopts a rear end feedback self-balancing structure, and the pilot oil path is communicated with a pilot end of each gear shift slide valve.
Preferably, a small filter screen and a throttle hole are arranged between the pilot oil path and the pilot end of the shift slide valve.
Preferably, the oil passage switching spool valve is controlled by a solenoid valve.
Preferably, a back pressure valve is connected to the oil path switching spool.
The invention discloses a gear shifting hydraulic control system, comprising: the oil tank is used for providing hydraulic oil; the main oil circuit outputs hydraulic oil from the oil tank, and the first gear shifting main oil circuit and the second gear shifting main oil circuit are connected with the oil tank; an oil passage switching spool for switching the first shift main oil passage and the second shift main oil passage; the first gear shifting main oil path and the second gear shifting main oil path are selectively communicated with a gear shifting slide valve to enable hydraulic oil to be selectively input into a piston cavity of a gear shifting fork; each gear shifting fork can selectively form gears synchronously with the gear gears, each gear comprises seven forward gears and one reverse gear, the odd gears of the gear shifting forks are arranged on the same odd-numbered gear output shaft, and the even gears and the reverse gears of the gear shifting forks are arranged on the other even-numbered gear output shaft; a gear hydraulic interlocking structure is arranged between the gear shifting slide valves of the two gear shifting forks acting on the odd-numbered gear output shafts or the even-numbered gear output shafts; the gear shifting slide valve is provided with a pilot end and a spring end, the pilot end is communicated with the oil tank through a pilot oil path, the hydraulic interlocking structure is a hydraulic interlocking oil path, one end of the hydraulic interlocking oil path is communicated with the pilot end of one gear shifting slide valve, and the other end of the hydraulic interlocking oil path is communicated with the spring end of the other gear shifting slide valve.
Preferably, each of the shift spools has a solenoid valve for controlling the movement of the spool to determine the size of the opening thereof, and the pilot oil path of the pilot end thereof is communicated with a pilot oil pressure control spool through a small strainer and an orifice.
Preferably, the pilot oil pressure control spool has a rear end feedback self-balancing structure, dynamic balance is achieved through hydraulic pressure of a pilot end of the pilot oil pressure control spool and spring force of a spring end of the pilot oil pressure control spool, hydraulic oil with stable pressure is formed by adjusting the size of openings of the spool and a valve body matching hole, and the hydraulic oil is communicated to the pilot end of the gear shift spool through a pilot oil path.
The invention also discloses a gearbox which comprises the shifting hydraulic control system.
The invention has the following beneficial effects:
1. the pilot oil pressure control slide valve can provide stable pilot pressure for the whole gear shifting system, the pilot pressure cannot fluctuate due to fluctuation of main oil pressure, the shift slide valve can be smoothly pushed to move under the action of the electromagnetic valve, hydraulic oil is controlled to smoothly push the shift fork to move, and good gear shifting smoothness is achieved;
2. the hydraulic interlocking device has the hydraulic interlocking function of the same output shaft gear, only one gear is combined on the same output shaft, and the damage of the gearbox caused by the formation of two gears on the same output shaft due to the misoperation of the electromagnetic valve is avoided;
3. the electromagnetic valve of the gear shifting slide valve and the electromagnetic valve of the oil path switching slide valve are of the same type, the size and the specification of the gear shifting slide valve are of the same type, and the type and the specification of the spring are consistent, so that the gear shifting slide valve has good interchangeability.
Drawings
The technical scheme of the invention is further explained by combining the drawings as follows:
FIG. 1: the hydraulic schematic diagram of the gear shifting hydraulic control system of the gearbox is shown;
wherein: f1-a first gear shifting fork, F2-a second gear shifting fork, F3-a third gear shifting fork and F4-a fourth gear shifting fork; 1-a first gear shifting slide valve, 2-a second gear shifting slide valve, 3-a third gear shifting slide valve, 4-a fourth gear shifting slide valve, 5-an oil way switching slide valve, 6-a pilot oil pressure control slide valve, 7-a hydraulic interlocking oil way and 8-a backpressure valve; s1, a first electromagnetic valve, S2, a second electromagnetic valve, S3, a third electromagnetic valve, S4, a fourth electromagnetic valve and S5, a fifth electromagnetic valve; a-main oil path, b-first gear-shifting main oil path, c-second gear-shifting main oil path and d-pilot oil path.
Detailed Description
The present invention will be described in detail below with reference to specific embodiments shown in the drawings. These embodiments are not intended to limit the present invention, and structural, methodical, or functional changes that may be made by one of ordinary skill in the art in light of these embodiments are intended to be within the scope of the present invention.
As shown in fig. 1, the present invention discloses a shift hydraulic control system comprising: the oil tank is used for providing hydraulic oil; a main oil path a for outputting hydraulic oil from an oil tank, and a first gear-shifting main oil path b and a second gear-shifting main oil path c; there is an oil passage switching spool valve 5 controlled by a solenoid valve S5, and the oil passage switching spool valve 5 can selectively switch the main oil passage a to communicate with the first shift main oil passage b or the second shift main oil passage c. The solenoid valve S5 linearly controls the current by the TCU. The oil path switching slide valve 5 is connected with a back pressure valve 8, so that hydraulic oil is always available in an oil path without oil supply after the main oil path is switched, and the whole hydraulic gear shifting control system is favorable for quickly establishing oil pressure.
The first gear-shifting main oil path b and the second gear-shifting main oil path c are selectively communicated with gear-shifting slide valves, so that hydraulic oil is selectively input into piston cavities of gear-shifting forks, each gear-shifting fork can selectively form gears synchronously with gear gears, the gear gears comprise seven forward gear gears and one reverse gear, odd-numbered gear gears of the gear-shifting forks are arranged on the same odd-numbered gear output shaft, and even-numbered gear gears and reverse gear gears of the gear-shifting forks are arranged on the other even-numbered gear output shaft.
Specifically, the preferred embodiment of the present invention has four shift forks, which are a first shift fork F1, a second shift fork F2, a third shift fork F3, and a fourth shift fork F4, respectively. Wherein, the first gear shifting fork F1 is used for controlling the corresponding synchronizer to form gears synchronously with the 1-gear or the 5-gear, the second gear shifting fork F2 is used for controlling the corresponding synchronizer to form gears synchronously with the 3-gear or the 7-gear, the third gear shifting fork F3 is used for controlling the corresponding synchronizer to synchronously form gears with the R-gear or the 4-gear, and the fourth gear shifting fork F4 is used for controlling the corresponding synchronizer to synchronously form gears with the 2-gear or the 6-gear. Each shift fork is controlled by a shift slide valve, respectively a first shift slide valve 1, a second shift slide valve 2, a third shift slide valve 3, a fourth shift slide valve 4. For example, when the hydraulic oil in the main oil line enters a piston chamber for controlling the 3-gear through the second shift spool 2, the second shift fork F2 is pushed to control the corresponding synchronizer to shift synchronously with the 3-gear to form the gear.
Each gear shifting slide valve is provided with a pilot end and a spring end, and the pilot ends are communicated with the oil tank through electromagnetic valves for controlling pilot oil paths. Preferably, each of the shift spools 1, 2, 3, 4 has a solenoid valve S1, S2, S3, S4 for controlling the movement of its spool to determine the opening size thereof, and the pilot oil path of its pilot end is communicated with the pilot oil pressure control spool 6. A gear hydraulic interlocking structure is arranged between the gear shifting slide valves of the two gear shifting forks acting on the odd-numbered gear output shafts or the even-numbered gear output shafts; the hydraulic interlocking structure is a hydraulic interlocking oil path, one end of the hydraulic interlocking oil path is communicated with the pilot end of one gear shifting slide valve, and the other end of the hydraulic interlocking oil path is communicated with the spring end of the other gear shifting slide valve. For example: the first gear shifting slide valve 1 and the second gear shifting slide valve 2 are matched with the odd-numbered gear output shaft, a hydraulic interlocking structure is arranged between the first gear shifting slide valve 1 and the second gear shifting slide valve 2, the hydraulic interlocking structure is a hydraulic interlocking oil path 7, one end of the hydraulic interlocking oil path 7 is communicated with the pilot end of the first gear shifting slide valve 1, and the other end of the hydraulic interlocking oil path is communicated with the spring end of the second gear shifting slide valve 2. There is also a hydraulic interlock arrangement between the mating shift spool valves on the even numbered output shafts.
The main oil path is also provided with a branch which is a pilot oil path d, hydraulic oil in the main oil path enters the pilot oil path d through a pilot oil pressure control slide valve 6, the pilot oil pressure control slide valve 6 adopts a rear end feedback self-balancing structure, and the pilot oil path is communicated with a pilot end of each gear shift slide valve. And a small filter screen and a throttle orifice are arranged between the pilot oil way and the pilot end.
The method specifically comprises the following steps: the pressure oil of the main oil path a is decompressed by the pilot oil pressure control slide valve 6 to provide pressure oil for the pilot end of the valve, and the valve core of the main oil path a has a certain cross section area, so that a certain pressure is formed between the pressure oil and the pressure oil acting on the pilot end of the valve, the valve core is pushed to overcome the spring force of the other end, and the forces at the two ends interact with each other, so that a stable dynamic balance relationship is achieved. When the pressure of the main oil path a rises, the flow rate of the hydraulic oil flowing through the pilot oil pressure control spool 6 increases, the pressure after passing through the pilot oil pressure control spool 6 also rises, at this time, the pressure of the pilot oil acting on the pilot oil pressure control spool 6 also rises, under the action of the pilot oil, the pilot oil pressure control spool 6 pushes the spool to move toward the spring end under the action of the hydraulic pressure, at this time, the opening area of the hydraulic oil entering the pilot oil pressure control spool 6 decreases, the flow rate of the hydraulic oil flowing through the valve decreases, the pressure of the hydraulic oil after passing through the valve decreases, the pressure of the pilot oil acting on the valve decreases, under the action of the spring force, the spool moves in the opposite direction, the area of the hydraulic oil flowing through the spool increases, and the pressure after passing through the valve is always stabilized in a dynamic balance. When the main circuit pressure decreases, it works in a similar manner to when it increases.
The operation of the preferred embodiment of the present invention is briefly described below.
The oil tank supplies oil through a main oil path a, the position of an oil path switching slide valve 5 is controlled through a fifth electromagnetic valve S5 to respectively supply oil to a first gear shifting main oil path b and a second gear shifting main oil path c, when the electromagnetic valve of the oil path switching control valve is controlled to have no current, the first gear shifting main oil path b can supply oil to four gears of 4 gears, 5 gears, 6 gears and 7 gears, when the electromagnetic valve S5 of the oil path switching slide valve 5 is controlled to reach a certain current, the oil path switching slide valve 5 switches the oil path, and the second gear shifting main oil path c supplies oil to four gears of R gears, 1 gear, 2 gears and 3 gears.
The hydraulic oil of the main oil path a passes through the pilot oil pressure control slide valve 6 and then respectively comprises: the first gear shifting slide valve 1, the second gear shifting slide valve 2, the third gear shifting slide valve 3, the fourth gear shifting slide valve 4 and the oil path switching slide valve 5 provide stable pilot oil, smooth switching of the oil path switching slide valve 5 is guaranteed, and pilot oil for controlling the gear shifting slide valves is not affected by fluctuation of main oil pressure.
Before the gear is not formed, the first gear shifting slide valve 1, the second gear shifting slide valve 2, the third gear shifting slide valve 3 and the fourth gear shifting slide valve 4 are all in a left position under the action of spring force. The position movements of the first gear shifting slide valve 1, the second gear shifting slide valve 2, the third gear shifting slide valve 3, the fourth gear shifting slide valve 4 and the oil path switching slide valve 5 are respectively controlled by electromagnetic valves S1, S2, S3, S4 and S5, and the corresponding oil path switching is carried out by controlling the movement of the gear shifting slide valve position, thereby completing the gear switching.
Because the synchronous forming gear gears forming the 1 gear, the 3 gear, the 5 gear and the 7 gear are on the same shaft, the synchronous forming gear gears forming the R gear, the 2 gear, the 4 gear and the 6 gear are on the same shaft, in order to avoid simultaneously forming two gears on the same output shaft due to misoperation of the electromagnetic valve and further causing damage of a gearbox or abnormal running of the whole vehicle, the hydraulic interlocking mode is utilized to respectively carry out hydraulic protection on the 1 gear, the 3 gear, the 5 gear and the 7 gear, and simultaneously, the same mode is adopted to carry out hydraulic interlocking protection on the R gear, the 2 gear, the 4 gear and the 6 gear.
The specific gear shifting is as follows: taking the 1-gear as an example, hydraulic oil enters a main oil path a, the electromagnetic valve S5 is electrified at the moment, the pilot end of the oil path switching slide valve 5 forms a closed cavity, pilot pressure is established, the oil path switching slide valve 5 is pushed to overcome the spring force to move left, the valve works at the right position, the second-gear oil path c is communicated, and the first-gear oil path b is cut off at the moment. The electromagnetic valve S1 works, a closed containing cavity is formed at the pilot end of the first gear shifting slide valve 1, pilot oil pressure is established, the first gear shifting slide valve 1 is pushed to move leftwards by overcoming spring force, the second gear shifting main oil way c is communicated with a piston cavity for controlling the gear 1, the piston pushes the gear shifting fork to move, and the gear 1 is quickly and smoothly formed under the control of the electromagnetic valve. Meanwhile, the pilot oil pressure of the pilot end of the first gear shifting slide valve 1 acts on the spring end of the second gear shifting slide valve 2, and the second gear shifting slide valve 2 is ensured to be in the left position together with the spring, at the moment, even if the solenoid valve S2 malfunctions, the pilot end of the second gear shifting slide valve 2 has oil pressure, and as the oil pressure of the spring end of the gear shifting slide valve is larger than or equal to the pilot pressure of the pilot end, the spring end has the effect of spring force at the same time, hydraulic oil can not enter a piston cavity leading to 3 and 7 gears, and the situation that two pairs of gears synchronously form gears on the same shaft is avoided. Similarly, when the gear 3 is formed, the oil ways for controlling the gear 1, the gear 5 and the gear 7 are all in a cut-off state, and the control mode forms hydraulic interlocking and provides guarantee for the normal operation of the gearbox.
Before the 1 gear is upgraded to the 2 gear, the pre-selection gear of the 2 gear is finished, the working principle of the pre-selection gear is the same as that of the 1 gear, namely the 1 gear is upgraded to the 2 gear, the electromagnetic valve S5 is electrified, the pilot end of the oil path switching slide valve 5 establishes pilot pressure, the oil path switching slide valve 5 is pushed to overcome the spring force to move left, the valve is enabled to work at the right position, the second gear oil path c is communicated, and at the moment, the first gear oil path b is cut off. At this time, immediately after that, the current of the solenoid valve S1 of the first shift spool 1 is controlled to 0A, and the oil passage controlled by the first shift spool 1 is in a cut-off state. The electromagnetic valve for controlling the fourth gear shifting slide valve 4 controls the current by TCU linearly at the moment and gradually reaches the maximum value, hydraulic oil acts on a piston cavity for controlling the 2 gears, the piston moves to push a shifting fork to move smoothly, and the 2 gears are formed quickly and smoothly. The pilot end of the fourth shift spool 4 builds up oil pressure, pushing the fourth shift spool 4 to move to the left, and at the same time, the pilot oil acting on the fourth shift spool 4 acts on the spring end of the shift valve C, so that the oil paths controlling the R range and the 4 range are in a cut-off state. Similarly, when the 4-gear is formed, the R-gear, the 2-gear and the 6-gear are in the cut-off state. The hydraulic interlocking protection mode is the same as the hydraulic interlocking protection mode, so that the situation that two gears are formed simultaneously due to the misoperation of the electromagnetic valve on the same shaft is avoided, and the risk of damage to the gearbox is avoided.
The invention has the following beneficial effects:
1. the pilot oil pressure control slide valve can provide stable pilot pressure for the whole gear shifting system, the pilot pressure cannot fluctuate due to fluctuation of main oil pressure, the shift slide valve can be smoothly pushed to move under the action of the electromagnetic valve, the flow and the pressure of hydraulic oil are controlled by controlling the sizes of the slide valve and the opening of the matching hole, the shift fork is smoothly pushed to move, and good gear shifting smoothness is achieved;
2. the invention has the hydraulic interlocking function of the same output shaft gear, only one gear is combined on the same output shaft, and the damage of the gearbox caused by the misoperation of the electromagnetic valve is avoided;
3. the electromagnetic valve of the gear shifting slide valve and the electromagnetic valve of the oil path switching slide valve are of the same type, the size and the specification of the gear shifting slide valve are of the same type, and the type and the specification of the spring are consistent, so that the gear shifting slide valve has good interchangeability.
The invention also discloses a gearbox comprising a gear shifting hydraulic control system in any form as described above.
It should be understood that although the present description refers to embodiments, not every embodiment contains only a single technical solution, and such description is for clarity only, and those skilled in the art should make the description as a whole, and the technical solutions in the embodiments can also be combined appropriately to form other embodiments understood by those skilled in the art.
The above-listed detailed description is only a specific description of a possible embodiment of the present invention, and they are not intended to limit the scope of the present invention, and equivalent embodiments or modifications made without departing from the technical spirit of the present invention should be included in the scope of the present invention.
Claims (8)
1. The gear shifting hydraulic control system comprises an oil tank for providing hydraulic oil, a main oil way (a) for outputting the hydraulic oil from the oil tank, and a group of gear shifting forks driven by the hydraulic oil, wherein the gear shifting forks are used for selectively forming gears synchronously with gear gears through synchronizers, each gear comprises seven forward gears and a reverse gear, an odd gear of each gear is arranged on the same odd gear output shaft, and an even gear of each gear and a reverse gear of each gear are arranged on the other even gear output shaft, and the gear shifting hydraulic control system is characterized in that: comprises that
The gear shifting fork mechanism comprises gear shifting slide valves and electromagnetic valves, wherein the number of the gear shifting slide valves is equal to that of the gear shifting fork mechanisms, and the electromagnetic valves are used for controlling each gear shifting slide valve;
the hydraulic oil in the main oil path (a) is selectively input into a first gear shifting main oil path (b) and a second gear shifting main oil path (c) in a piston cavity of a gear shifting fork;
an oil passage switching spool (5) for switching the first shift main oil passage (b) and the second shift main oil passage (c);
the main oil way (a) is also provided with a branch which is a pilot oil way (d), hydraulic oil in the main oil way (a) enters the pilot oil way (d) through a pilot oil pressure control slide valve (6), the pilot oil pressure control slide valve (6) adopts a rear end feedback self-balancing structure, and the pilot oil way (d) is communicated with a pilot end of each gear shifting slide valve;
the hydraulic interlocking device comprises four gear shifting forks and four gear shifting slide valves corresponding to the gear shifting forks, wherein every two pairs of the gear shifting slide valves and the gear shifting forks act on the same output shaft, each gear shifting slide valve is provided with an electromagnetic valve for controlling the valve core of the gear shifting slide valve to move, a pilot end and a spring end, the pilot end is communicated with an oil tank through the electromagnetic valve, a hydraulic interlocking structure is a hydraulic interlocking oil path arranged between the two gear shifting slide valves acting on the same output shaft, one end of the hydraulic interlocking oil path is communicated with the pilot end of one of the gear shifting slide valves, and the other end of the hydraulic interlocking oil path is communicated with the spring end of the other gear shifting slide valve.
2. The shift hydraulic control system according to claim 1, characterized in that: and a small filter screen and a throttle orifice are arranged between the pilot oil path (d) and the pilot end of the gear shifting slide valve.
3. The shift hydraulic control system according to any one of claim 2, wherein: the oil path switching slide valve (5) is controlled by an electromagnetic valve (S5).
4. The shift hydraulic control system according to claim 3, characterized in that: the oil path switching slide valve (5) is connected with a back pressure valve (8).
5. A shift hydraulic control system characterized by: comprises that
The oil tank is used for providing hydraulic oil;
a main oil path (a) for outputting hydraulic oil from an oil tank, a first gear-shifting main oil path (b) and a second gear-shifting main oil path (c);
an oil passage switching spool (5) for switching the first shift main oil passage (b) and the second shift main oil passage (c);
the first gear shifting main oil path (b) and the second gear shifting main oil path (c) are selectively communicated with a gear shifting slide valve to enable hydraulic oil to be selectively input into a piston cavity of a gear shifting fork;
each gear shifting fork can be selectively synchronized with a gear through a synchronizer to form a gear, the gear gears comprise seven forward gears and a reverse gear, odd gears of the gear shifting forks are arranged on the same odd-numbered gear output shaft, and even gears and the reverse gear of the gear shifting forks are arranged on the other even-numbered gear output shaft;
a gear hydraulic interlocking structure is arranged between the gear shifting slide valves of the two gear shifting forks acting on the odd-numbered gear output shafts or the even-numbered gear output shafts;
the gear shifting slide valve is provided with a pilot end and a spring end, the pilot end is communicated with the corresponding electromagnetic valve and the corresponding oil tank through a pilot oil path (d), the hydraulic interlocking structure is a hydraulic interlocking oil path, one end of the hydraulic interlocking oil path is communicated with the pilot end of one gear shifting slide valve, and the other end of the hydraulic interlocking oil path is communicated with the spring end of the other gear shifting slide valve.
6. The shift hydraulic control system according to claim 5, characterized in that: each gear shifting slide valve is provided with an electromagnetic valve for controlling the valve core to move to determine the opening size of the gear shifting slide valve, and a pilot oil path (d) at the pilot end of the gear shifting slide valve is communicated with a pilot oil pressure control slide valve (6) through a small filter screen and a throttling hole.
7. The shift hydraulic control system according to claim 6, characterized in that: the pilot oil pressure control slide valve (6) is provided with a rear end feedback self-balancing structure, dynamic balance is achieved through hydraulic pressure of a pilot end of the pilot oil pressure control slide valve and spring force of a spring end of the pilot oil pressure control slide valve, hydraulic oil with stable pressure is formed by adjusting the size of openings of the slide valve and a valve body matching hole, and the hydraulic oil is communicated to the pilot end of the gear shifting slide valve through a pilot oil way (d).
8. Gearbox, its characterized in that: comprising a shifting hydraulic control system according to any one of claims 1 to 7.
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| CN201710374126.9A CN107435733B (en) | 2017-05-24 | 2017-05-24 | Gear shifting hydraulic control system and gearbox |
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| CN201710374126.9A CN107435733B (en) | 2017-05-24 | 2017-05-24 | Gear shifting hydraulic control system and gearbox |
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Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03209056A (en) * | 1990-01-09 | 1991-09-12 | Kubota Corp | Working vehicle running shifting structure |
| DE102009005756A1 (en) * | 2009-01-23 | 2010-07-29 | Daimler Ag | Control device for an automated change-speed gearbox |
| CN101858431A (en) * | 2010-04-17 | 2010-10-13 | 浙江吉利汽车研究院有限公司 | Hydraulic device for gear shift of double-clutch automatic transmission |
| DE102011100849A1 (en) * | 2011-05-06 | 2012-11-08 | Audi Ag | Double clutch |
| CN102338217A (en) * | 2011-07-18 | 2012-02-01 | 吉林大学 | Electric control pneumatic mechanical automatic shift system |
| CN202612588U (en) * | 2011-12-29 | 2012-12-19 | 长城汽车股份有限公司 | Hydraulic gear-shifting control system for double clutch transmission |
| CN206874805U (en) * | 2017-05-24 | 2018-01-12 | 捷孚传动科技有限公司 | Gear shifting hydraulic control system and gearbox |
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2017
- 2017-05-24 CN CN201710374126.9A patent/CN107435733B/en active Active
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