CN108757611A - Multi-speed automatic transmission hydraulic system - Google Patents
Multi-speed automatic transmission hydraulic system Download PDFInfo
- Publication number
- CN108757611A CN108757611A CN201810899547.8A CN201810899547A CN108757611A CN 108757611 A CN108757611 A CN 108757611A CN 201810899547 A CN201810899547 A CN 201810899547A CN 108757611 A CN108757611 A CN 108757611A
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- Prior art keywords
- valve
- pressure
- oil circuit
- control
- proportion magnetic
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 33
- 230000001050 lubricating effect Effects 0.000 claims abstract description 28
- 238000001816 cooling Methods 0.000 claims abstract description 27
- 238000005461 lubrication Methods 0.000 claims abstract description 12
- 239000012530 fluid Substances 0.000 claims abstract description 11
- 239000003921 oil Substances 0.000 claims description 75
- 239000000872 buffer Substances 0.000 claims description 20
- 239000010720 hydraulic oil Substances 0.000 claims description 7
- 230000005611 electricity Effects 0.000 claims description 5
- 230000005906 menstruation Effects 0.000 claims description 3
- 230000001737 promoting effect Effects 0.000 claims description 3
- 238000004891 communication Methods 0.000 claims description 2
- 238000005303 weighing Methods 0.000 claims description 2
- 238000005516 engineering process Methods 0.000 description 9
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 229910052742 iron Inorganic materials 0.000 description 2
- 238000001228 spectrum Methods 0.000 description 2
- 238000000418 atomic force spectrum Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000000306 component Substances 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 210000003739 neck Anatomy 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
-
- 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
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/4043—Control of a bypass valve
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Control Of Transmission Device (AREA)
Abstract
The invention discloses a kind of multi-speed automatic transmission hydraulic systems, including：Electronic pump, mechanical pump, principal pressure oil circuit and cooling and lubricating circuit, shift control oil circuit is connected on principal pressure oil circuit, electronic pump is connected to principal pressure oil circuit with the oil outlet of mechanical pump, the oil outlet of principal pressure oil circuit is connect with pressure valve, the oil outlet of pressure valve controls oil circuit connection with cooling and lubricating circuit and shift respectively, electromagnet proportional control valve is provided on principal pressure oil circuit, system principal pressure is controlled by electromagnet ratio realizes pressure control, lubrication counterbalance valve is provided on cooling and lubricating circuit, the excess flow of pressure valve is controlled by lubricating counterbalance valve and front end load, regime flow is provided to cooling and lubricating circuit.By the above-mentioned means, multi-speed automatic transmission hydraulic system of the present invention effectively reduces hydraulic pressure loss using double pump system, start and stop ride comfort is improved, is directly driven using electromagnet, cost advantage is apparent, and the locking of fluid torque-converter uses flow control, precision higher.
Description
Technical field
The present invention relates to automatic transmission technical fields, more particularly to a kind of multi-speed automatic transmission hydraulic system.
Background technology
Four big core components one of of the automatic transmission as automobile, are monopolized by foreign technology always, in the recent period Japan's love
Letter with it is lucky equal joint, have the tendency that thoroughly closing down domestic independently automatic transmission industry greatly.To find out its cause, automatic transmission
Core technology missing be domestic independent research automatic transmission pain spot.
As the core technology of automatic transmission, hydraulic system is always that domestic automatic transmission needs the bottleneck broken through,
The country lies substantially in imitation and plagiarizes the stage of foreign technology at present, domestic current as the core technology of automatic transmission
Rarely has the enterprise for capableing of autonomous completely new positive development.
Multi-speed automatic transmission is at present using the 6AT of love letter and ZF as mainstream, and hydraulic system is extremely complex, several years ago by electricity
The influence of magnet valve technology and other control technologies, for hydraulic system generally by the way of pilot control, love believes newest release
Its hydraulic system of 09G6AT automatic transmission uses straight drive magnetic valve, hydraulic system to obtain prodigious simplification.
But straight drive magnetic valve Costco Wholesale is high at present, if domestic use straight drive magnetic valve entirely from basic transmission enterprise, by
It is small in yield, it is with high costs.It is of high cost using straight drive magnetic valve, while higher, hydraulic pressure are required to the cleannes of entire speed changer
The installation of valve block must be carried out in the dust-free workshop of high request, and the abrasion of speed changer, also easily lead to abrasion impurity and entered
Hydraulic system causes solenoid valve clamping stagnation, and then the failures such as shift shock for causing speed changer, and the new energy of Guangzhou Automobile Workshop's independent development is certainly
Speed changer is moved using straight drive magnetic valve just often to occur because of failure caused by solenoid valve clamping stagnation.
Invention content
The invention mainly solves the technical problem of providing a kind of multi-speed automatic transmission hydraulic systems, using double pump system
System effectively reduces hydraulic pressure loss, improves the ride comfort of start and stop, hydraulic system realizes simplification to greatest extent, and reliability is more
Height is directly driven using electromagnet, and cost advantage is apparent, and the locking of fluid torque-converter uses flow control, precision higher.
In order to solve the above technical problems, one aspect of the present invention is：A kind of multi-speed automatic transmission is provided
Hydraulic system, including：Electronic pump, mechanical pump, principal pressure oil circuit and cooling and lubricating circuit are connected with shift control on principal pressure oil circuit
The oil outlet of liquefaction road, electronic pump and mechanical pump is connected to principal pressure oil circuit, and the oil outlet of principal pressure oil circuit is connect with pressure valve,
The oil outlet of pressure valve controls oil circuit connection with cooling and lubricating circuit and shift respectively,
Electromagnet proportional control valve is provided on principal pressure oil circuit, pressure valve connects electromagnet proportional control valve, and pressure valve passes through
Adjusting and control to system principal pressure are realized in the control of electromagnet proportional control valve,
It is provided with lubrication counterbalance valve on cooling and lubricating circuit, the excess flow of pressure valve is by lubricating counterbalance valve and front end load
Control provides stable cooling and lubricating flow to cooling and lubricating circuit.
In a preferred embodiment of the present invention, the oil outlet of electronic pump is provided with the first check valve, and mechanical pump goes out
Oil port is provided with the second check valve, and electronic pump and mechanical pump are installed in parallel the oiler in principal pressure oil circuit.
In a preferred embodiment of the present invention, adjusting and control range of the electromagnet proportional control valve to system principal pressure
For 3 ~ 20bar.
In a preferred embodiment of the present invention, access has fluid torque-converter, TC lock valves, oil cooling on cooling and lubricating circuit
Device and clutch, when TC locking valve deblockings：
Hydraulic oil on principal pressure oil circuit is directly entered clutch offer active lubrication by pressure valve rear portion and dynamic pressure is flat
Weighing apparatus, another part enter oil cooler after excess pressure torque-converters, and cooling and lubrication is provided for Bearing gear.
In a preferred embodiment of the present invention, shift control oil circuit is connected to principal pressure oil circuit, shift control by pressure valve
Liquefaction road is provided with and the main solenoid valve of principal pressure oil communication, the first proportion magnetic valve, the second proportion magnetic valve, third ratio
Example solenoid valve, the 4th proportion magnetic valve and the 5th proportion magnetic valve,
Oil circuit is controlled by shift after hydraulic oil promoting menstruation excess pressure valve on principal pressure oil circuit and supplies main solenoid valve, the first ratio electricity
Magnet valve, the second proportion magnetic valve, third proportion magnetic valve, the 4th proportion magnetic valve and the 5th proportion magnetic valve are realized to clutch
The pressure of device is controlled and is adjusted.
In a preferred embodiment of the present invention, electromagnet proportional control valve, main solenoid valve, the first proportion magnetic valve,
Two proportion magnetic valves, third proportion magnetic valve, the 4th proportion magnetic valve and the 5th proportion magnetic valve are straight drive magnet control
Valve directly drives spool by electromagnet and carries out pressure adjusting.
In a preferred embodiment of the present invention, the control pressure of the active area and clutch at electromagnet effect end is directly driven
Directly proportional, the valve core diameter of control valve and valve port are directly proportional to clutch control flow.
In a preferred embodiment of the present invention, the control moving range for directly driving magnet control valve is 0 ~ 2mm, solenoid valve
Power is 0 ~ 23N.
In a preferred embodiment of the present invention, further include third check valve, third check valve on shift control oil circuit
It is arranged at the drain tap of clutch.
In a preferred embodiment of the present invention, the first buffer, the second ratio electricity are connected on the first proportion magnetic valve
It is connected with the second buffer on magnet valve, third buffer is connected on third proportion magnetic valve, is connected on the 4th proportion magnetic valve
There is the 4th buffer, the 5th buffer is connected on the 5th proportion magnetic valve.
The beneficial effects of the invention are as follows：Multi-speed automatic transmission hydraulic system of the present invention uses double pump system, effectively reduces
Hydraulic pressure is lost, and improves the ride comfort of start and stop, hydraulic system realizes simplification, reliability higher, using electromagnetism to greatest extent
Iron directly drives, and cost advantage is apparent, and the locking of fluid torque-converter uses flow control, precision higher.
Description of the drawings
To describe the technical solutions in the embodiments of the present invention more clearly, make required in being described below to embodiment
Attached drawing is briefly described, it should be apparent that, drawings in the following description are only some embodiments of the invention, for
For those of ordinary skill in the art, without creative efforts, it can also be obtained according to these attached drawings other
Attached drawing, wherein：
Fig. 1 is that the multi-speed automatic transmission hydraulic pressure system of the present invention unifies the structural schematic diagram of preferred embodiment；
The label of each component is as follows in attached drawing：100, electronic pump, the 101, first check valve, 200, mechanical pump, 201, second is unidirectional
Valve, 300, principal pressure oil circuit, 301, pressure valve, 302, electromagnet proportional control valve, 400, cooling and lubricating circuit, 401, the lubrication back of the body
Pressure valve, 402, fluid torque-converter, 403, TC lock valves, 404, oil cooler, 500, shift control oil circuit, the 501, first ratio electromagnetism
Valve, the 502, second proportion magnetic valve, 503, third proportion magnetic valve, the 504, the 4th proportion magnetic valve, the 505, the 5th ratio electromagnetism
Valve, 506, main solenoid valve, 507, third check valve, the 508, first buffer, the 509, second buffer, 510, third buffer,
511, the 4th buffer, the 512, the 5th buffer, 600, clutch.
Specific implementation mode
The technical scheme in the embodiments of the invention will be clearly and completely described below, it is clear that described implementation
Example is only a part of the embodiment of the present invention, instead of all the embodiments.Based on the embodiments of the present invention, this field is common
All other embodiment that technical staff is obtained without making creative work belongs to the model that the present invention protects
It encloses.
Referring to Fig. 1, the embodiment of the present invention includes：
A kind of multi-speed automatic transmission hydraulic system, including：Electronic pump 100, mechanical pump 200, principal pressure oil circuit 300 and cooling profit
Road 400 is slid back to, shift control oil circuit 500 is connected on principal pressure oil circuit 300, the oil outlet of electronic pump 100 and mechanical pump 200 is equal
It is connected to principal pressure oil circuit 300, the oil outlet of principal pressure oil circuit 300 is connect with pressure valve 301, the oil outlet difference of pressure valve 301
It is connect with cooling and lubricating circuit 400 and shift control oil circuit 500.
The oil outlet of electronic pump 100 is provided with the first check valve 101, and the oil outlet of mechanical pump 200 is provided with second
Check valve 201, electronic pump 100 and mechanical pump 200 are installed in parallel the oiler in principal pressure oil circuit 300.
The double oil pumps of system use, 100 1 mechanical pumps 200 of one of electronic pump, such advantage are：
The discharge capacity that mechanical pump 200 can be reduced, it is high-revolving in engine, it is unnecessary hydraulic system can be significantly reduced
Power attenuation；
In speed operation, electronic pump 100 can provide a system to supplement, and meet the flow demand of system；
Under start and stop operating mode, electronic pump 100 can also provide the minimum flow demand of system, ensure starting moment, vehicle energy
The rapid power that provides realizes starting, can greatly improve the ride comfort of start stop system in this way.
Electromagnet proportional control valve 302 is provided on principal pressure oil circuit 300, pressure valve 301 connects the control of electromagnet ratio
Valve 302, pressure valve 301 realize adjusting and control to system principal pressure, electromagnetism by the control of electromagnet proportional control valve 302
Iron proportional control valve 302 is 3 ~ 20bar to the adjusting of system principal pressure and control range, it can be achieved that the pressure of 3 ~ 20bar controls.
Shift control oil circuit 500 is connected to principal pressure oil circuit 300 by pressure valve 301, is provided on shift control oil circuit 500
The main solenoid valve 506 that is connected to principal pressure oil circuit 300, the first proportion magnetic valve 501, the second proportion magnetic valve 502, third ratio
Solenoid valve 503, the 4th proportion magnetic valve 504 and the 5th proportion magnetic valve 505, the hydraulic oil promoting menstruation on principal pressure oil circuit 300
Oil circuit 500 is controlled by shift after pressure valve 301 and supplies main solenoid valve 506, the first proportion magnetic valve 501, the second ratio electromagnetism
Valve 502, third proportion magnetic valve 503, the 4th proportion magnetic valve 504 and the 5th proportion magnetic valve 505 realize the pressure to clutch
Power is controlled and is adjusted.
Electromagnet proportional control valve 302, main solenoid valve 506, the first proportion magnetic valve 501, the second proportion magnetic valve 502,
Third proportion magnetic valve 503, the 4th proportion magnetic valve 504 and the 5th proportion magnetic valve 505 are straight drive magnet control valve, are led to
It crosses electromagnet and directly drives spool progress pressure adjusting.
The straight active area for driving electromagnet effect end is directly proportional to the control pressure of clutch 600, and the spool of control valve is straight
Diameter and valve port are directly proportional to clutch control flow.
Preferably, the current range for directly driving magnet control valve is 0 ~ 1.3A, and resistance range is 0 ~ 6.1 Ω, and outer diameter is
28mm, length 34mm, control moving range are 0 ~ 2mm, and solenoid valve power is 0 ~ 23N.
The straight magnet control valve that drives has high-precision, low sluggish, electric electromagnetism force curve optional, is suitable for diversified connection
Device, quality it is high have advantage.
The control of clutch 600, which is all made of electromagnet and directly drives spool, adjusts out required control pressure, according to reality
The size requirement of border pressure can adjust the size of spool feedback end to realize different demands of the different clutches 600 to pressure, use
The pressure demand of clutch brake can be completely covered in straight drive electromagnet selected by the present invention, pressure regulation spectrum.
The control of clutch 600 is directly driven using electromagnet, since the electromagnetic force of electromagnet only has 20N or so, needs to realize
The design of the pressure output of 20bar or so, spool is very crucial, and the design of clutch control spool is by that will export control pressure
Force feedback acts on end to electromagnet, the pressure output of 0 ~ 20bar can be easily realized by adjusting the active area of feedback end, together
When by the adjustment of valve core diameter and valve port size, can easily meet the instantaneous big flow demand that clutch combines moment.
Further include third check valve 507 on shift control oil circuit 500, third check valve 507 is arranged in clutch 600
At drain tap.The drain tap of clutch 600 all devises the third check valve 507 of low-pressure, to ensure that clutch cavity is protected always
The state for holding oil is remarkably improved response speed when clutch combines in this way.
It is connected with the first buffer 508 on first proportion magnetic valve 501, is connected with second on the second proportion magnetic valve 502
It is connected with third buffer 510 on buffer 509, third proportion magnetic valve 503, is connected on the 4th proportion magnetic valve 504
Four buffers 511 are connected with the 5th buffer 512 on the 5th proportion magnetic valve 505, can improve the comfort of shift in this way,
Reduce hydraulic pressure loss.
Lubrication counterbalance valve 401 is provided on cooling and lubricating circuit 400, the excess flow of pressure valve 301 is by lubricating back pressure
The control of valve 401 and front end load provides stable cooling and lubricating flow to cooling and lubricating circuit.
Hydraulic oil from electronic pump 100 and mechanical pump 200 adjusts oil by the pressure valve 301 on principal pressure oil circuit 300
After pressure, it is delivered to lubrication counterbalance valve 401 from the oil outlet of pressure valve 301, by being supplied to cooling and lubricating after lubricating counterbalance valve 401
Circuit.
Access has fluid torque-converter 402, TC lock valves 403, oil cooler 404 and clutch on cooling and lubricating circuit 400
When 600, TC lock valves 403 unlock：Hydraulic oil on principal pressure oil circuit 300 by 301 rear portion of pressure valve be directly entered from
Clutch 600 provides active lubrication and kinetic pressure balancing, and another part enters oil cooler 404 after excess pressure torque-converters 402, is bearing
Gear provides cooling and lubrication.
The locking of fluid torque-converter 404 carries out independent fuel feeding, and this torque-converters can effectively reduce the efficiency damage of torque-converters
Consumption.
The locking of fluid torque-converter 404 uses individual flow control mode, and the gentler combination of torque-converters may be implemented：
Momentary traffic demand when due to 404 locking of fluid torque-converter is bigger than ordinary clutch, and the diameter design of spool is also big
In common clutch pressure control valve.
The advantageous effect of multi-speed automatic transmission hydraulic system of the present invention is：
Using double pump system, the application of electronic pump can effectively reduce the discharge capacity of mechanical pump on traditional automatic transmission, to drop
Low hydraulic power loss unnecessary under high engine speeds operating mode, under start and stop operating mode, electronic pump can also provide a system to
Minimum flow demand effectively reduces hydraulic pressure loss, improves the ride comfort of start and stop；
Hydraulic system realizes simplification, reliability higher to greatest extent；
Directly driven using electromagnet, according to the size requirement of actual pressure, the size of adjustable spool feedback end come realize it is different from
Clutch brake is to the different demands of pressure, and the pressure demand of clutch brake can be completely covered in pressure regulation spectrum, full
While sufficient performance requirement, cost can control lower；
The locking of fluid torque-converter uses flow control, precision higher that the gentler combination of torque-converters may be implemented.
Example the above is only the implementation of the present invention is not intended to limit the scope of the invention, every to utilize this hair
Equivalent structure or equivalent flow shift made by bright description is applied directly or indirectly in other relevant technology necks
Domain is included within the scope of the present invention.
Claims (10)
1. a kind of multi-speed automatic transmission hydraulic system, which is characterized in that including：Electronic pump, mechanical pump, principal pressure oil circuit and cold
But lubricating loop, shift control oil circuit is connected on principal pressure oil circuit, and electronic pump is connected to principal pressure with the oil outlet of mechanical pump
The oil outlet of oil circuit, principal pressure oil circuit is connect with pressure valve, and the oil outlet of pressure valve is controlled with cooling and lubricating circuit and shift respectively
Oil circuit connection processed,
Electromagnet proportional control valve is provided on principal pressure oil circuit, pressure valve connects electromagnet proportional control valve, and pressure valve passes through
Adjusting and control to system principal pressure are realized in the control of electromagnet proportional control valve,
It is provided with lubrication counterbalance valve on cooling and lubricating circuit, the excess flow of pressure valve is by lubricating counterbalance valve and front end load
Control provides stable cooling and lubricating flow to cooling and lubricating circuit.
2. multi-speed automatic transmission hydraulic system according to claim 1, which is characterized in that the oil outlet of electronic pump is set
It is equipped with the first check valve, the oil outlet of mechanical pump is provided with the second check valve, and electronic pump and mechanical pump are installed in parallel in main pressure
The oiler of power oil circuit.
3. multi-speed automatic transmission hydraulic system according to claim 1, which is characterized in that electromagnet proportional control valve pair
The adjusting of system principal pressure and control range are 3 ~ 20bar.
4. multi-speed automatic transmission hydraulic system according to claim 1, which is characterized in that cooling and lubricating accesses on circuit
There are fluid torque-converter, TC lock valves, oil cooler and a clutch, when TC locking valve deblockings：
Hydraulic oil on principal pressure oil circuit is directly entered clutch offer active lubrication by pressure valve rear portion and dynamic pressure is flat
Weighing apparatus, another part enter oil cooler after excess pressure torque-converters, and cooling and lubrication is provided for Bearing gear.
5. multi-speed automatic transmission hydraulic system according to claim 1, which is characterized in that shift control oil circuit passes through pressure
Power valve is connected to principal pressure oil circuit, is provided on shift control oil circuit and the main solenoid valve of principal pressure oil communication, the first ratio electricity
Magnet valve, the second proportion magnetic valve, third proportion magnetic valve, the 4th proportion magnetic valve and the 5th proportion magnetic valve,
Oil circuit is controlled by shift after hydraulic oil promoting menstruation excess pressure valve on principal pressure oil circuit and supplies main solenoid valve, the first ratio electricity
Magnet valve, the second proportion magnetic valve, third proportion magnetic valve, the 4th proportion magnetic valve and the 5th proportion magnetic valve are realized to clutch
The pressure of device is controlled and is adjusted.
6. multi-speed automatic transmission hydraulic system according to claim 5, which is characterized in that electromagnet proportional control valve,
Main solenoid valve, the first proportion magnetic valve, the second proportion magnetic valve, third proportion magnetic valve, the 4th proportion magnetic valve and the 5th ratio
Example solenoid valve is straight drive magnet control valve, and directly driving spool by electromagnet carries out pressure adjusting.
7. multi-speed automatic transmission hydraulic system according to claim 6, which is characterized in that the straight electromagnet that drives acts on end
Active area is directly proportional to the control pressure of clutch, and the valve core diameter of control valve and valve port and clutch control flow are at just
Than.
8. multi-speed automatic transmission hydraulic system according to claim 7, which is characterized in that straight drive magnet control valve
Control moving range is 0 ~ 2mm, and solenoid valve power is 0 ~ 23N.
9. multi-speed automatic transmission hydraulic system according to claim 5, which is characterized in that on shift control oil circuit also
Including third check valve, third check valve is arranged at the drain tap of clutch.
10. multi-speed automatic transmission hydraulic system according to claim 5, which is characterized in that on the first proportion magnetic valve
It is connected with the first buffer, the second buffer is connected on the second proportion magnetic valve, is connected with third on third proportion magnetic valve
It is connected with the 4th buffer on buffer, the 4th proportion magnetic valve, the 5th buffer is connected on the 5th proportion magnetic valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810899547.8A CN108757611B (en) | 2018-08-09 | 2018-08-09 | Hydraulic system of multi-gear automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810899547.8A CN108757611B (en) | 2018-08-09 | 2018-08-09 | Hydraulic system of multi-gear automatic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108757611A true CN108757611A (en) | 2018-11-06 |
| CN108757611B CN108757611B (en) | 2024-04-26 |
Family
ID=63969515
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810899547.8A Active CN108757611B (en) | 2018-08-09 | 2018-08-09 | Hydraulic system of multi-gear automatic transmission |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110388452A (en) * | 2019-07-26 | 2019-10-29 | 奇瑞汽车股份有限公司 | Hydraulic feed system, control method and automobile |
| CN111853228A (en) * | 2020-07-27 | 2020-10-30 | 浙江轩孚自动变速器有限公司 | Hydraulic control system of automatic transmission |
| CN112461109A (en) * | 2020-11-10 | 2021-03-09 | 中国北方车辆研究所 | On-line measuring device for abrasion loss of gear shifting sliding block of gear shifting control mechanism |
| CN113417997A (en) * | 2021-07-02 | 2021-09-21 | 贵州凯星液力传动机械有限公司 | Clutch and oil cylinder integrated control hydraulic system |
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| CN208778373U (en) * | 2018-08-09 | 2019-04-23 | 江苏金润汽车传动科技有限公司 | Multi-speed automatic transmission hydraulic system |
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| CN103115148A (en) * | 2013-01-31 | 2013-05-22 | 湖南江麓容大车辆传动股份有限公司 | Vehicle and automatic transmission and hydraulic control system of automatic transmission |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111853228A (en) * | 2020-07-27 | 2020-10-30 | 浙江轩孚自动变速器有限公司 | Hydraulic control system of automatic transmission |
| CN111853228B (en) * | 2020-07-27 | 2021-11-12 | 浙江轩孚自动变速器有限公司 | Hydraulic control system of automatic transmission |
| CN112461109A (en) * | 2020-11-10 | 2021-03-09 | 中国北方车辆研究所 | On-line measuring device for abrasion loss of gear shifting sliding block of gear shifting control mechanism |
| CN113417997A (en) * | 2021-07-02 | 2021-09-21 | 贵州凯星液力传动机械有限公司 | Clutch and oil cylinder integrated control hydraulic system |
| CN113417997B (en) * | 2021-07-02 | 2023-01-20 | 贵州凯星液力传动机械有限公司 | Clutch and oil cylinder integrated control hydraulic system |
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| CN108757611B (en) | 2024-04-26 |
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