CN101566204A - Intermediate shaft brake of reversing valve pump control type automatic transmission - Google Patents
Intermediate shaft brake of reversing valve pump control type automatic transmission Download PDFInfo
- Publication number
- CN101566204A CN101566204A CNA2009100433505A CN200910043350A CN101566204A CN 101566204 A CN101566204 A CN 101566204A CN A2009100433505 A CNA2009100433505 A CN A2009100433505A CN 200910043350 A CN200910043350 A CN 200910043350A CN 101566204 A CN101566204 A CN 101566204A
- Authority
- CN
- China
- Prior art keywords
- oil
- automatic transmission
- valve
- intermediate shaft
- reversing valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Landscapes
- Control Of Transmission Device (AREA)
Abstract
The invention discloses an intermediate shaft brake of a reversing valve pump control type automatic transmission, comprising a hydraulic pump, a two-position three-way electromagnetic reversing valve electrically connected with an automatic transmission TCU, an oil inlet connected with the hydraulic pump, an oil outlet connected with an oil tank directly, and another oil outlet connected with an oil inlet of a constant pressure overflow valve; an oil return opening of the constant pressure overflow valve is connected with the oil tank and an oil inlet thereof is connected with an oil outlet of the two-position three-way electromagnetic reversing valve. The invention has the beneficial effects as follows: 1. during the brake of the intermediate shaft of the automatic transmission, the heat generated by energy loss is taken away by the hydraulic oil so as to provide a stable and accurate braking torque; 2. abrasion is basically not generated, the service life is long and the maintenance cost is effectively decreased; and 3. no power source is needed and simple structure is provided.
Description
Technical field
The present invention relates to a kind of jack shaft braking device of automatic transmission, especially the intermediate shaft brake of middle shaft type electric-controlled mechanical automatic speed transmission (AMT).
Background technique
Electric control mechanical type automatic speed variator (AMT) is a body with traditional manual transmission, and its gear-shifting actuating mechanism then changes electronic control mode into by traditional manual control mode.Shaft type had a grade gear transmission in the middle of ripe manual transmission mostly adopted, and by changing the engagement of gear train, changed velocity ratio, reached the purpose of speed change.When automobile when low grade rises up into top grade, clutch is in separated state, gear train is in neutral state, this moment, jack shaft was appointed the high speed rotating state that is in because of the reason of inertia, its rotating speed is higher than the high-grade gear that will mesh, and rises up into top grade by force and can cause and beat the tooth phenomenon.In order to reduce shifting shock, to shorten shift time, automatic transmission is equipped with intermediate shaft brake, forces to reduce the jack shaft rotating speed, rises up into top grade when jack shaft and high-grade gear rotational speed difference are little.At present, known intermediate shaft brake adopts multi-disc wet clutch structure commonly used, mainly form by piston, pressing plate, friction plate, solenoid valve, hydraulic power elements such as (or gas pressure sourcies), wherein friction plate and jack shaft connect by spline, with identical rotating speed rotation, and pressing plate can not be rotated by the brake casing restriction.When needs are braked jack shaft, transmission control unit (TCU) sends signal and makes the electromagnetic valve coil energising, piston axially moves under the effect of hydraulic pressure (or air pressure), make pressing plate and friction plate combine closely, frictional force between pressing plate and the friction plate makes the rotating speed of jack shaft sharply descend, and reaches the purpose of brake intermediate shaft.Obviously, there is following some deficiency in above-mentioned break: 1, friction plate long-term work, and cause that easily temperature sharply raises, thereby cause the variation of friction factor, influence braking effect, also be unfavorable for sequencing control; 2, friction plate weares and teares easily, needs periodic replacement, because speed changer in case of transmission, be dismantled, the maintenance cost height in the mounting point; 3, complex structure, manufacturing and installation cost are higher.
Summary of the invention
The present invention is unfavorable for sequencing control, safeguards, makes the installation cost problem of higher in order to solve existing intermediate shaft brake, the invention provides a kind of reversing valve pump control type automatic transmission intermediate shaft brake.
The objective of the invention is to realize in the following way: a kind of reversing valve pump control type automatic transmission intermediate shaft brake comprises an oil hydraulic pump; A two-bit triplet solenoid directional control valve, this two-bit triplet solenoid directional control valve is electrically connected with automatic transmission TCU, filler opening is connected with oil hydraulic pump, oil outlet directly connects fuel tank, another oil outlet connects level pressure relief valve filler opening, the return opening of level pressure relief valve connects fuel tank, and filler opening links to each other with an oil outlet of two-bit triplet solenoid directional control valve.
The hydraulic pressure pump delivery is 10～15ml/r.
Latus rectum 6～the 12mm of two-bit triplet solenoid directional control valve.
The force value of level pressure relief valve is 1.5～2MPa.
Oil hydraulic pump, two-bit triplet solenoid directional control valve and the serial of level pressure relief valve are provided with, and are the hydraulic pressure oil duct therebetween.
The present invention installs an oil hydraulic pump at the output terminal of transmission countershaft, drives the cylinder block of hydraulic pumps rotation with jack shaft, and this oil hydraulic pump is as the deceleration loading of jack shaft; The oil hydraulic pump outlet connects the filler opening of a two-bit triplet solenoid directional control valve, and an oil outlet of solenoid directional control valve directly connects fuel tank, and another oil outlet connects a level pressure relief valve filler opening, and level pressure relief valve return opening connects fuel tank; Transmission control unit (TCU) sends the voltage of SC sigmal control selector valve coil, with the path of change oil hydraulic pump outlet fluid, thus the effective acting time of control jack shaft retarding torque.When not needing brake intermediate shaft, the coil voltage that TCU sends the SC sigmal control solenoid directional control valve is zero, and solenoid directional control valve works in " upper ", the direct oil sump tank of oil hydraulic pump outlet fluid, the pressure of oil hydraulic pump outlet is zero, and the jack shaft non-brake torque does not have energy loss certainly yet; When the needs brake intermediate shaft, the coil voltage that TCU sends the SC sigmal control solenoid directional control valve is a load voltage value, solenoid directional control valve works in " the next ", oil hydraulic pump outlet fluid need be by level pressure relief valve ability backflow fuel tank, this moment, the pressure of oil hydraulic pump outlet was corresponding definite value, and retarding torque also is a corresponding definite value, and the jack shaft rotating speed descends at once, by the current"on"time control brake torque effective acting time of control solenoid directional control valve, reach the purpose of brake intermediate shaft.The invention has the beneficial effects as follows: 1, can in the braking of automatic transmission jack shaft, take away the heat that produces because of energy loss, a stable and accurate retarding torque is provided by hydraulic oil; 2, essentially no wearing and tearing, long service life effectively reduces maintenance cost; 3, do not need power source, simple in structure.
Description of drawings
Fig. 1 is a structural representation of the present invention;
Fig. 2 is the present invention and one 4 gear gearbox connection diagram;
Among the figure, 1. transmission input shaft, 2. input shaft gear, 3. one grade of gear, 4. one, the second gear combined cover, 5. intermediate gear, 6. three-range transmission, 7. three, the fourth gear combined cover, 8. fourth gear, 9. reverse gear, 10. reverse gear combined cover, 11. transmission output shaft, 12. reverse idler gears, 13. transmission countershafts, 14. oil hydraulic pump, 15. fuel tanks, 16. solenoid directional control valves, 17. the level pressure relief valve, 18. engine output shafts, 19. clutches.
Embodiment
As shown in Figure 1, a kind of reversing valve pump control type automatic transmission intermediate shaft brake comprises an oil hydraulic pump 14; A two-bit triplet solenoid directional control valve 16, this two-bit triplet solenoid directional control valve 16 is electrically connected with automatic transmission TCU, filler opening is connected with oil hydraulic pump 14, oil outlet directly connects fuel tank, another oil outlet connects level pressure relief valve 17 filler openings, the return opening of level pressure relief valve [17] connects fuel tank, and filler opening links to each other with an oil outlet of two-bit triplet solenoid directional control valve 16; The discharge capacity of oil hydraulic pump 14 is 10～15ml/r; Latus rectum 6～the 12mm of two-bit triplet solenoid directional control valve 16; The force value of level pressure relief valve 17 is 1.5～2Mpa; Oil hydraulic pump 14, two-bit triplet solenoid directional control valve 16 and the 17 serial settings of level pressure relief valve are the hydraulic pressure oil duct therebetween.
As shown in Figure 2,4 gear gearboxes comprise transmission input shaft 1,2, one grades of gears 3, of input shaft gear, second gear combined cover 4, intermediate gear 5, three-range transmission 6, three, fourth gear combined cover 7, fourth gear 8, reverse gear 9, reverse gear combined cover 10, transmission output shaft 11, reverse idler gear 12, transmission countershaft 13, when speed changer (being sake of clarity, is example to rise up into second gear from one grade) when low grade rises up into top grade, at first, clutch 19 separates, and interrupts the power transmission between engine output shaft 18 and the transmission input shaft 1; Then, one, second gear combined cover 4 moves to right and no longer combine with one grade of gear 3, is in neutral gear position, interrupt the power transmission of transmission countershaft 13 and transmission output shaft 11.Next action, promptly be with one, second gear combined cover 4 moves to right again, and it is combined with intermediate gear 5, makes transmission countershaft 13 and transmission output shaft 11 pass through intermediate gear 5 transferring power.In this process because effect of inertia, transmission countershaft 13 after entering the neutral operation, still keeping one grade in conjunction with the time rotating speed, promptly intermediate gear 5 is also keeping corresponding rotating speed; Be subjected to the influence of inertia equally, one, second gear combined cover 4 keeping one grade in conjunction with the time corresponding rotating speed.Obviously, because the difference of speed ratio between the gear mesh, the rotating speed of intermediate gear 5 will be higher than one, the rotating speed of second gear combined cover 4, in order not cause shifting shock, prolongs the working life of gear, expects both synchronization.For making both synchronization, need brake transmission countershaft 13, as calculated, this retarding torque is that 40～60N.m is more satisfactory.
The present invention utilizes a hydraulic-pressure pump 14, a solenoid directional control valve 16 and a level pressure relief valve 17 to provide retarding torque for transmission countershaft 13, can adopt various ways such as spline, flat key or flange to connect between hydraulic-pressure pump 14 and the transmission countershaft 13, the rotor that jack shaft 13 drives hydraulic-pressure pump 14 rotates synchronously, pumps fluid.The oil outlet of hydraulic-pressure pump 14 connects the inlet of solenoid directional control valve 16, and an oil outlet of solenoid directional control valve 16 directly connects fuel tank, and another oil outlet connects level pressure relief valve 17 filler openings, and level pressure relief valve 17 return openings connect fuel tank 15.Obviously, when solenoid directional control valve 16 worked in " upper ", oil hydraulic pump 14 outlet fluid were by the direct oil sump tank of this valve, the pressure of hydraulic oil is extremely low, the driving torque that oil hydraulic pump 14 needs is zero substantially, and for transmission countershaft 13, suffered retarding torque also approaches zero; When solenoid directional control valve 16 works in " the next ", oil hydraulic pump 14 outlet fluid are by level pressure relief valve 17 ability backflow fuel tanks, because the effect of level pressure relief valve 17, oil hydraulic pump 14 outlet oil pressure will keep a definite value, the driving torque that oil hydraulic pump 14 needs also is a definite value, for transmission countershaft 13, suffered retarding torque also keeps a definite value.Therefore, when not needing, only need control solenoid directional control valve 16, make this valve work in " upper ", the outlet oil pressure of oil hydraulic pump 14 is reduced to zero by TCU to jack shaft 13 braking; When needs are braked, by TCU control solenoid directional control valve 16, make this valve work in " the next ", the outlet oil pressure of oil hydraulic pump 14 is remained on a definite value, regulate its action time according to brake request and get final product.As calculated, provide 40～60N.m desirable retarding torque, the common relief valve that the common two-bit triplet solenoid directional control valve of only need the discharge capacity normal hydraulic oil pump that is 10～15ml, 6～12mm latus rectum, pressure are 1.5～2MPa gets final product; Simultaneously, the heat that braking process produces is taken away in real time by hydraulic oil, without any need for cooling unit.The present invention realizes easily, and is simple in structure, with low cost.
Claims (5)
1, a kind of reversing valve pump control type automatic transmission intermediate shaft brake is characterized in that: comprise an oil hydraulic pump [14]; A two-bit triplet solenoid directional control valve [16], this two-bit triplet solenoid directional control valve [16] is electrically connected with automatic transmission TCU, filler opening is connected with oil hydraulic pump [14], oil outlet directly connects fuel tank, another oil outlet connects level pressure relief valve [17] filler opening, the return opening of level pressure relief valve [17] connects fuel tank, and filler opening links to each other with an oil outlet of two-bit triplet solenoid directional control valve [16].
2. a kind of reversing valve pump control type automatic transmission intermediate shaft brake according to claim 1 is characterized in that: the discharge capacity of oil hydraulic pump [14] is 10～15ml/r.
3, a kind of reversing valve pump control type automatic transmission intermediate shaft brake according to claim 1 is characterized in that: the latus rectum 6～12mm of two-bit triplet solenoid directional control valve [16].
4, a kind of reversing valve pump control type automatic transmission intermediate shaft brake according to claim 1, it is characterized in that: the force value of level pressure relief valve [17] is 1.5～2MPa.
5, a kind of reversing valve pump control type automatic transmission intermediate shaft brake according to claim 1 is characterized in that: oil hydraulic pump [14], two-bit triplet solenoid directional control valve [16] and level pressure relief valve [17] serial setting are the hydraulic pressure oil duct therebetween.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2009100433505A CN101566204A (en) | 2009-05-11 | 2009-05-11 | Intermediate shaft brake of reversing valve pump control type automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2009100433505A CN101566204A (en) | 2009-05-11 | 2009-05-11 | Intermediate shaft brake of reversing valve pump control type automatic transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101566204A true CN101566204A (en) | 2009-10-28 |
Family
ID=41282522
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2009100433505A Pending CN101566204A (en) | 2009-05-11 | 2009-05-11 | Intermediate shaft brake of reversing valve pump control type automatic transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101566204A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105782288A (en) * | 2016-05-24 | 2016-07-20 | 中国重汽集团大同齿轮有限公司 | Intermediate shaft brake for AMT automatic mechanical speed changer |
| CN106438526A (en) * | 2016-11-12 | 2017-02-22 | 湘潭大学 | Electric proportional control type rock drill impacting pressure automatic control system |
| CN114458759A (en) * | 2022-02-22 | 2022-05-10 | 一汽解放汽车有限公司 | Control method of AMT intermediate shaft brake based on oil pump |
| CN115013520A (en) * | 2022-06-17 | 2022-09-06 | 潍柴动力股份有限公司 | AMT gearbox intermediate shaft brake control method, device and controller |
-
2009
- 2009-05-11 CN CNA2009100433505A patent/CN101566204A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105782288A (en) * | 2016-05-24 | 2016-07-20 | 中国重汽集团大同齿轮有限公司 | Intermediate shaft brake for AMT automatic mechanical speed changer |
| CN106438526A (en) * | 2016-11-12 | 2017-02-22 | 湘潭大学 | Electric proportional control type rock drill impacting pressure automatic control system |
| CN106438526B (en) * | 2016-11-12 | 2017-11-14 | 湘潭大学 | A kind of electric proportional control formula rock drill surge automatic control system |
| CN114458759A (en) * | 2022-02-22 | 2022-05-10 | 一汽解放汽车有限公司 | Control method of AMT intermediate shaft brake based on oil pump |
| CN115013520A (en) * | 2022-06-17 | 2022-09-06 | 潍柴动力股份有限公司 | AMT gearbox intermediate shaft brake control method, device and controller |
| CN115013520B (en) * | 2022-06-17 | 2024-05-17 | 潍柴动力股份有限公司 | AMT gearbox intermediate shaft braking control method, device and controller |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102979862B (en) | Two gear formula automatic transmission | |
| CN1325296C (en) | Synchronous device for double clutch speed variator | |
| CN102562968B (en) | Automatic transmission driving device for unpowered interrupted gear-shifting and gear-shifting control method thereof | |
| CN102230534B (en) | Hydraulic control system for double-clutch automatic gearbox | |
| US20070000339A1 (en) | Drive train of a motor vehicle | |
| CN101566202A (en) | Intermediate shaft brake of proportional valve control pump type automatic speed changer | |
| CN101566204A (en) | Intermediate shaft brake of reversing valve pump control type automatic transmission | |
| CN101949430A (en) | Novel double clutch type automatic transmission (DCT) layout structure | |
| CN101566203B (en) | Intermediate shaft brake of hydraulic retarding type automatic speed changer | |
| CN201992052U (en) | Double-clutch control device for double-clutch automatic gearbox | |
| CN101280826A (en) | Power shift type automatic transmission system | |
| WO2022173858A4 (en) | Multi-speed turbine reduction gearbox system and method | |
| CN202926977U (en) | Two-gear automatic transmission | |
| CN105793607A (en) | Speed change mechanism with gears overlap | |
| CN202326847U (en) | Proportional valve-controlled pump type intermediate shaft brake for automatic transmission | |
| CN201547211U (en) | Hydraulic speed changer | |
| CN103968012B (en) | Loader three clutch gearbox | |
| CN103032545B (en) | Dual-clutch automatic hydraulic clutch | |
| CN205064625U (en) | Automatic hydraulic clutch based on manual shifting gear box | |
| CN105736652A (en) | Double-clutch type automatic transmission | |
| CN2599318Y (en) | Power transfer hydraulic speed variator | |
| CN201963765U (en) | Automatic clutch for configurating motor vehicle with manual gear box | |
| CN203822964U (en) | Three clutch gearbox for loading machine | |
| CN203823035U (en) | Three clutch gearbox for medium and small sized loading machine | |
| CN202883823U (en) | Automatic hydraulic clutch based on automatic shifting gear box |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Open date: 20091028 |