CN115182990B - Hydraulic control system for hybrid hydraulic automatic gearbox - Google Patents
Hydraulic control system for hybrid hydraulic automatic gearbox Download PDFInfo
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- CN115182990B CN115182990B CN202210631335.8A CN202210631335A CN115182990B CN 115182990 B CN115182990 B CN 115182990B CN 202210631335 A CN202210631335 A CN 202210631335A CN 115182990 B CN115182990 B CN 115182990B
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- 238000005461 lubrication Methods 0.000 claims abstract description 28
- 238000002156 mixing Methods 0.000 claims abstract description 11
- 239000003921 oil Substances 0.000 claims description 303
- 239000012530 fluid Substances 0.000 claims description 23
- 238000004891 communication Methods 0.000 claims description 9
- 230000005540 biological transmission Effects 0.000 claims description 8
- 239000010687 lubricating oil Substances 0.000 claims description 4
- 239000012141 concentrate Substances 0.000 claims 3
- 239000013589 supplement Substances 0.000 abstract description 2
- 238000013461 design Methods 0.000 description 14
- 238000000034 method Methods 0.000 description 10
- 101150006573 PAN1 gene Proteins 0.000 description 8
- 238000001914 filtration Methods 0.000 description 8
- 239000012535 impurity Substances 0.000 description 7
- 238000001816 cooling Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 5
- 238000011010 flushing procedure Methods 0.000 description 5
- 238000000227 grinding Methods 0.000 description 4
- 238000011161 development Methods 0.000 description 3
- 239000010729 system oil Substances 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000003749 cleanliness Effects 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000003860 storage Methods 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 238000003475 lamination Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000036632 reaction speed Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
- F16H61/0025—Supply of control fluid; Pumps therefore
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0402—Cleaning of lubricants, e.g. filters or magnets
- F16H57/0404—Lubricant filters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
- F16H57/0435—Pressure control for supplying lubricant; Circuits or valves therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
- F16H57/0446—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control the supply forming part of the transmission control unit, e.g. for automatic transmissions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
- F16H61/0025—Supply of control fluid; Pumps therefore
- F16H61/0031—Supply of control fluid; Pumps therefore using auxiliary pumps, e.g. pump driven by a different power source than the engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/2807—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted using electric control signals for shift actuators, e.g. electro-hydraulic control therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
- F16H2061/0034—Accumulators for fluid pressure supply; Control thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
- F16H2061/0037—Generation or control of line pressure characterised by controlled fluid supply to lubrication circuits of the gearing
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
Abstract
The invention discloses a hydraulic control system for a hybrid hydraulic automatic gearbox, and belongs to the technical field of hydraulic control. The system comprises an oil pan, wherein the oil pan is connected with an oil filter-coarse oil outlet of which is connected with a mechanical pump and an electronic pump which are connected in parallel, and the oil outlets of the mechanical pump and the electronic pump are connected with a main oil way pressure control slide valve; the main oil way pressure control slide valve is respectively connected with a main oil pressure electromagnetic valve, a lubrication back pressure valve, a C0 pressure control slide valve and a pressure reducing valve; the lubrication back pressure valve is connected with a lubrication oil duct of the mixing module; the C0 pressure control slide valve is respectively connected with a C0 pressure measuring point, a C0 electromagnetic valve, a pressure reducing valve, a drain back pressure valve and a main oil pressure electromagnetic valve; the C0 electromagnetic valve is connected with the pressure reducing valve; the pressure reducing valve is connected with the oil draining back pressure valve. The system is relatively independent, the capacity of other systems is not increased to supplement the extra load generated by the hybrid power module, the resources of other systems of the vehicle are not obviously consumed, the main oil pressure is adjustable, and more types of gearboxes are easy to adapt.
Description
Technical Field
The invention belongs to the technical field of hydraulic control, and particularly relates to a hydraulic control system for a hybrid hydraulic automatic gearbox.
Background
The global climate is increasingly severe, and under the new regulations of increasingly strict carbon emission, the development of new energy automobiles becomes the mainstream trend. The running distance and the torque demand of the commercial vehicle are large, and the commercial vehicle is also a cost sensitive market. So the current mainstream trend is hybrid power assembly, can realize making changes on original vehicle platform, reduce development cost and risk. Meanwhile, the requirements of higher power, lower fuel consumption and lower emission in daily driving are met.
One development focus of the hybrid gearbox is the structure and arrangement of a hydraulic system, but because the hybrid power assembly of the hydraulic automatic gearbox has multiple driving modes and additional lubrication and cooling requirements, the additional hydraulic pumps of the vehicle are mutually interfered in a pure electric mode or a mode that a motor starts an engine to run, and the burden of other systems is increased; in addition, the main oil line oil pressure of the hydraulic system is not adjustable, cannot be compatible with oil pumps with different performances and cannot meet different pressure requirements of the C0 clutch in different vehicle modes.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention aims to provide a hydraulic control system and a hydraulic control method for a hybrid hydraulic automatic gearbox, which solve the problems that the mutual interference between additional hydraulic pumps is caused when a vehicle runs in a pure electric mode or a motor starts an engine, the oil pressure of a main oil way of a hydraulic system is not adjustable, the hydraulic system cannot be compatible with oil pumps with different performances, and the problem that a C0 clutch has different pressure requirements in different vehicle modes cannot be solved.
In order to achieve the above purpose, the invention is realized by adopting the following technical scheme:
the invention discloses a hydraulic control system for a hybrid hydraulic automatic gearbox, which comprises an oil pan, an oil filter-coarse, a mechanical pump, an electronic pump, a main oil pressure electromagnetic valve, a main oil way pressure control slide valve, a lubrication back pressure valve, a C0 pressure control slide valve, a C0 electromagnetic valve, a pressure reducing valve and a drainage back pressure valve;
the oil pan is communicated with the oil filter-coarse oil inlet, the mechanical pump and the electronic pump are connected in parallel, the oil inlets of the mechanical pump and the electronic pump are communicated with the oil filter-coarse oil outlet, and the oil outlets of the mechanical pump and the electronic pump are communicated with the main oil way pressure control slide valve; the main oil way pressure control slide valve is respectively connected with the main oil pressure electromagnetic valve, the lubrication back pressure valve, the C0 pressure control slide valve and the pressure reducing valve; the lubrication back pressure valve is connected with the lubrication oil duct of the mixing module; the C0 pressure control slide valve is respectively connected with a C0 pressure measuring point, a C0 electromagnetic valve, a pressure reducing valve, a drain back pressure valve and a main oil pressure electromagnetic valve; the C0 electromagnetic valve is connected with the pressure reducing valve; the pressure reducing valve is connected with the oil draining back pressure valve.
Preferably, an accumulator is also provided, which is connected to the C0 pressure control spool and the C0 solenoid valve, respectively.
Preferably, an oil filter-essence is further arranged, an oil inlet of the oil filter-essence is communicated with oil outlets of the mechanical pump and the electronic pump, and an oil outlet of the oil filter-essence is communicated with the main oil way pressure control slide valve.
Preferably, the main oil path pressure control slide valve has pilot control oil paths X1 and X2, the port A1 of the main oil pressure solenoid valve is in fluid connection with port A2 of the main oil pressure solenoid valve, the port A1 of the main oil path pressure control slide valve is branched off into the pilot control oil path X2, the port P2 of the main oil pressure solenoid valve and the main oil path m, the port B of the main oil path pressure control slide valve is led to the lubricating oil path, and the port A1 of the main oil path pressure control slide valve is respectively communicated with the port P4 of the C0 pressure control slide valve and the port P7 of the pressure reducing valve through the main oil path m.
Preferably, the oil outlet of the electronic pump is also provided with a one-way valve.
Preferably, the main oil pressure solenoid valve and the C0 solenoid valve are both proportional solenoid valves.
Preferably, the main oil pressure solenoid valve and the C0 solenoid valve are two-position three-way, direct proportion solenoid valves.
Preferably, an orifice is provided between the outlet of the C0 pressure control spool and the inlet of the accumulator.
Preferably, the pilot control X4 of the C0 pressure control spool is in fluid communication with port A6 of the C0 solenoid valve and port P5 of the accumulator; the A7 port of the pressure reducing valve is in fluid communication with the P6 port of the C0 solenoid valve.
The invention also discloses a vehicle comprising the hydraulic control system for the hybrid hydraulic automatic gearbox.
Compared with the prior art, the invention has the following beneficial effects:
the invention provides a hydraulic control system for a hybrid hydraulic automatic gearbox, wherein an oil pan provides a fluid source for the system, fluid is filtered through an oil filter-coarse filter, the hydraulic valve plate is prevented from being blocked by impurities, and the filtered fluid enters a mechanical pump and an electronic pump and becomes fluid with pressure. The parallel design of the mechanical pump and the electronic pump is used as an independent system, the electronic pump can share the work load for the mechanical pump when needed, the burden of other systems is not increased, the double-pump system is beneficial to reducing the size and weight of the required mechanical pump, the operation of the system in a complete electric mode can be met, and the problem of hybrid power multi-mode driving is effectively solved. In order to be compatible with the use of two oil pumps with different performances, the main oil pressure electromagnetic valve is connected in parallel on the basis of the main oil way pressure control slide valve, so that the main oil pressure can be regulated, the oil pumps with different performances are compatible, and the different pressure requirements of the C0 clutch under different vehicle modes and the use conditions of more hybrid power gearboxes are met. The lubrication back pressure valve and the arrangement of the oil drainage back pressure valve in the oil drainage oil way can ensure that oil does not flow back, and meanwhile, the oil way of the actuating element is not emptied when the hydraulic system does not work, so that the reaction speed of the whole hydraulic system is more sensitive. The connection of the main oil pressure solenoid valve and the C0 pressure control slide valve can provide oil with stable oil pressure for the pressure control valve. The setting of relief pressure valve can reduce the too big main oil circuit oil pressure to the setting value to guarantee that control oil circuit oil pressure satisfies the requirement, in order to reach more accurate oil pressure control. The system is relatively independent, the capacity of other systems is not increased to supplement the additional workload generated by the hybrid power module, the resources of other systems of the vehicle are not required to be consumed obviously, meanwhile, the independent design can reduce the design change of other systems (a lubricating system or an oil supply system and the like), the cost can be reduced, and more types of gearboxes can be easily adapted.
Further, the energy accumulator is arranged on the oil way of the hydraulic actuating element, so that the effects of steadily rising and quickly falling oil pressure can be achieved, the work of the actuating element is facilitated, and the gear shifting experience is better.
Further, the oil filter-essence can be used in combination with the oil filter-coarse filtration, and on the basis that the oil filter-coarse filtration of larger impurity particles is carried out, finer impurities can be filtered, so that the tiny impurities are prevented from entering the hydraulic valve plate module to cause valve core clamping stagnation, and the performance of the whole vehicle is influenced.
Drawings
FIG. 1 is a hydraulic schematic diagram of the hydraulic control system of the present invention with each hydraulic component not in operation;
FIG. 2 is a state diagram of the hydraulic control system of the present invention in operation;
FIG. 3 is a schematic diagram of the construction of a main oil solenoid valve and a main line pressure control spool in the hydraulic control system of the present invention;
FIG. 4 is a schematic diagram of the operation of the main oil solenoid valve and the main oil pressure control spool in the hydraulic control system of the present invention;
FIG. 5 is a schematic diagram of the configuration of the C0 solenoid valve, the C0 pressure control spool valve, and the accumulator in the hydraulic control system of the present invention;
fig. 6 is a schematic structural view of the working states of the C0 solenoid valve, the C0 pressure control spool valve and the accumulator in the hydraulic control system of the present invention.
Wherein: 1-an oil pan; 2-oil filter-coarse; 3-a mechanical pump; 4-an electronic pump; 5-oil filter-extract; 6-a main oil pressure solenoid valve; 7-a main oil way pressure control slide valve; 8-lubrication back pressure valve; 9-C0 pressure control spool valve; 10-an accumulator; 11-C0 solenoid valve; 12-a pressure reducing valve; 13-a drain back pressure valve; 14-C0 pressure tap.
Detailed Description
In order that those skilled in the art will better understand the present invention, a technical solution in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in which it is apparent that the described embodiments are only some embodiments of the present invention, not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the present invention without making any inventive effort, shall fall within the scope of the present invention.
It should be noted that the terms "comprises" and "comprising," along with any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed or inherent to such process, method, article, or apparatus, but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
The invention is described in further detail below with reference to fig. 1-6:
the invention provides a hydraulic control system for a hybrid hydraulic automatic gearbox, which comprises an oil pan 1, an oil filter-coarse 2, a mechanical pump 3, an electronic pump 4, an oil filter-fine 5, a main oil pressure electromagnetic valve 6, a main oil way pressure control slide valve 7, a lubrication back pressure valve 8, a C0 pressure control slide valve 9, an energy accumulator 10, a C0 electromagnetic valve 11, a pressure reducing valve 12 and an oil drainage back pressure valve 13.
As shown in fig. 1 and 2, the oil pan 1 provides a fluid source to provide separate oil for the hybrid module for circulation of the hydraulic system, and can be used as a stand-alone system without interfering with the oil of other systems. The oil pan 1 is communicated with the oil inlet of the oil filter-coarse 2, and the oil filter-coarse 2 is placed between the oil inlet formed by the mechanical pump 3 and the electronic pump 4 and the oil way of the oil pan 1 in a magnet mode, so that larger impurities can be filtered for system oil, and the cleanliness of the system oil entering the oil pump is ensured. The mechanical pump 3 and the electronic pump 4 are connected in parallel, the oil inlets of the mechanical pump 3 and the electronic pump 4 are connected in parallel, the oil outlets of the oil filter-coarse pump 2 are connected with the oil inlets of the mechanical pump 3 and the electronic pump 4, and when the mechanical pump 3 or the electronic pump 4 works, the fluid oil in the oil pan 1 is sucked into the oil filter-coarse pump 2 for first coarse filtration, and the fluid oil becomes pressure oil with pressure through the mechanical pump 3 or the electronic pump 4. The mechanical pump 3 provides pressure oil for the hydraulic system of the hybrid module, and the electronic pump 4 provides pressure oil for the hydraulic system of the hybrid module in the case that the engine is turned off and the hybrid module requires hydraulic oil. In order to prevent high-pressure oil from the oil outlet of the mechanical pump 3 from flowing into the electronic pump 4 when the mechanical pump is in operation, the oil outlet of the electronic pump 4 is further provided with a one-way valve which only allows fluid to flow from the oil inlet a to the oil outlet b of the electronic pump 4. The mechanical pump 3 is connected with the engine through the input shaft due to mechanical structure, and cannot reversely move by the oil pressure backflow of the electronic pump 4, so that the arrangement of a one-way valve is not needed. The oil outlets of the mechanical pump 3 and the electronic pump 4 are communicated with the oil filter-essence 5, the oil filter-essence 5 is external and can be replaced periodically, and high-pressure oil at the outlet of the mechanical pump 3 or the electronic pump 4 can be filtered through the oil filter-essence 5 and then enters the hydraulic valve plate. The hydraulic valve plate is a precise matching piece, very tiny oil impurities can lead to clamping stagnation of the valve core, the performance of the gearbox is influenced, on the basis that the oil filter-coarse 2 filters out larger impurities, the oil filter-fine 5 performs second-time filtration, two-stage filtration (coarse filtration and fine filtration) can better ensure the cleanliness of oil, the filtration precision is improved, the possibility of blockage of the hydraulic valve plate is reduced, and the performance and the service life of the system are ensured.
The oil outlet of the oil filter-essence 5 is communicated with the P1 oil inlet of the main oil way pressure control slide valve 7, the main oil pressure electromagnetic valve 6 and the main oil way pressure control slide valve 7 control and regulate the main oil way oil pressure (namely the A1 oil pressure of the main oil way pressure control slide valve 7) through coaction, and the combination regulation can be controlled by a controller to realize variable main oil way oil pressure so as to adapt to different use scenes. The main oil pressure control slide valve 7 has two paths of pilot control oil paths X1 and X2, X2 is the feedback oil pressure of an A1 port, X1 is in fluid connection with an A2 port of the main oil pressure electromagnetic valve 6, the pilot control oil pressure of the main oil pressure control slide valve 7 is the pilot control oil pressure, the main oil pressure electromagnetic valve 6 is a proportional electromagnetic valve, and the oil pressure of the A2 port can be controlled by an electric control system. As shown in fig. 3 and 4: the port A1 of the main oil pressure control spool 7 is branched into three paths of oil paths respectively entering the pilot control oil path X2, the port P2 of the main oil pressure solenoid valve 6 and the main oil path m (as shown in fig. 2), the port B of the main oil pressure control spool 7 is led to the lubrication oil path, the main oil pressure solenoid valve 6 is structurally and directly arranged directly above the main oil pressure control spool 7, and the oil outlet A2 of the main oil pressure solenoid valve 6 directly acts on the upper end surface of the main oil pressure control spool 7, namely the pilot control oil path X1 of the main oil pressure control spool 7. When the pressure oil from the oil pump (i.e., the mechanical pump 3 or the electronic pump 4) reaches the port P1 of the main oil passage pressure control spool 7, if the oil pressure is smaller than the design value P0, the spool is not moved, as shown in fig. 3, i.e., the port A1 oil pressure is equal to the port P1 oil pressure and is equal to the pilot control oil passage X2 oil pressure, the main oil pressure solenoid valve 6 is closed, P (X2) S is equal to or smaller than F (spring force), the spool is not moved, and the port B is the lubrication oil passage from which no fluid flows out. When the pressure of the port P1 of the main oil path pressure control slide valve 7 is greater than the design value P0, the oil pressure of the port A1 of the main oil path pressure control slide valve 7 is equal to the oil pressure of the port X2, at the moment, P (X2) S is greater than F (spring force), the valve core is forced to move downwards, the port A1 is communicated with the port B to start oil drainage to the lubricating oil duct, when the flow of fluid oil pumped by the oil pump increases, the oil pressure of the port P1 is increased to enable the valve core to move downwards continuously, the port A1 is communicated with the port B and the port T2 to drain oil further (as shown in fig. 4), and the oil pressure of the port A1 is further reduced to reach the design value P0. The pressure of the port A1 is reduced, the valve core is pushed upwards by the spring force of the valve core, the port A1 and the port T2 are not communicated, and the valve core can dynamically adjust the position all the time to keep the oil pressure of the port A1 never to exceed the design value p0. However, for the hydraulic system of the hybrid module, the capacity of the electronic pump 4 is generally weak, the flow rate and the oil pressure are low, and the design value p0 may not be reached. If the valve core is fixed in position under the condition, the port A1 has oil pressure, but the port B of the lubricating oil path has no fluid to pass through, so that the normal operation of the mixing module is not facilitated. At this time, the main oil pressure electromagnetic valve 6 can be opened, and the main oil pressure electromagnetic valve 6 can regulate the outlet oil pressure to linearly change according to the electromagnetic valve current, namely the X1 pilot control oil pressure to linearly change, so that the magnitude of the oil pressure of the opening A1 is controlled through the electric control system. The valve core with the structure that { p (X2) +p (X1) } is larger than F (spring force) can move downwards, the port B is communicated with the port A1, and because the oil pressure of the port A1 is changed linearly, the oil pressure of the port A1 can be achieved, the oil pressure of the port A1 can be changed in an adjustable way, the design value p0 is not a fixed value, and the flexible design can meet the use condition of more hybrid power gearboxes.
The P3 oil inlet of the lubrication back pressure valve 8 is in fluid communication with the B port of the main oil way pressure control slide valve 7 and the lubrication oil channel of the mixing module, the lubrication back pressure valve 8 is an overflow valve, the oil pressure of the main oil inlet P3 can be ensured to be stabilized at a design value, when the design value is exceeded, the main oil inlet P3 of the lubrication back pressure valve 8 is communicated with the main oil drain port T4, the oil pressure is reduced through oil drain, and when the design value is reduced, the spring force pushes the valve core to move so that the oil port is disconnected, namely the lubrication oil way is stabilized at a certain pressure.
The port A1 of the main oil line pressure control spool 7 is respectively communicated with the port P4 of the C0 pressure control spool 9 and the port P7 of the relief valve 12 through the main oil line m (fig. 2), so as to provide stable main oil pressure for the subsequent hydraulic system actuating element.
Fig. 5 and 6 are schematic structural views of the C0 solenoid valve 11, the C0 pressure control spool 9, and the accumulator 10, using a similar structure to the main oil passage control valve. The C0 electromagnetic valve 11 is directly arranged right above the C0 pressure control slide valve 9, and the pilot control X4 of the C0 pressure control slide valve 9 is in fluid communication with the A6 port of the C0 electromagnetic valve 11 and the P5 port of the accumulator 10, so that stable and controllable hydraulic oil can be provided for the hydraulic actuator C0. The C0 solenoid valve 11 is a proportional solenoid valve, and the oil pressure of the port A6 is controlled to be changed in proportion by an electric control system, so that the oil pressure of the pilot control X4 of the C0 pressure control spool 9 is affected to be changed in proportion. The C0 pressure control spool 9 linearly changes the A4 port oil pressure from 0 to the set value by the combined action of the pilot control X4, the feedback control X3, and the spring force. The accumulator 10 can stably control the oil pressure X4 of the C0 pressure control spool 9, so that the pressure is stable and free from abrupt change when the pressure is increased, and can quickly change from the maximum value to 0, thereby realizing the linear control of the clutch pressure of the hydraulic actuator C0. When the C0 solenoid valve 11 receives the output oil pressure of the current signal solenoid valve, i.e., the oil pressure of the pilot control oil passage of X4 of the C0 pressure control spool 9, as shown in fig. 6: p (A4 port oil pressure) ×s2+f (spring) =p (pilot X4) ×s1. (X3 feedback control oil pressure is equal to the A4 port oil pressure value) when p (pilot X4) linearly changes, p (A4 port) also linearly changes. An orifice with the diameter phi of 1.2mm is arranged between the oil pressure of the X4 outlet of the C0 pressure control slide valve 9 and the oil path of the inlet of the accumulator 10, so that the situation that the oil pressure of the A4 port changes too quickly, the clutch rushes out of oil too quickly and gear shifting impact occurs can be avoided; meanwhile, in the process of oil flushing, if the oil pressure fluctuates greatly, the energy accumulator 10 can play a role in stabilizing the oil pressure; when the C0 solenoid valve 11 receives a current signal of 0mA, the oil pressure of the port X4 is rapidly released to become 0, but at this time, the oil pressure of the port X4 does not become 0 very rapidly due to the accumulator 10, and the pressure oil stored in the accumulator 10 is slowly released through the orifice, so that the shift shock at the moment of clutch switching can be reduced, and the clutch is relatively slowly released.
The A7 oil port of the pressure reducing valve 12 is in fluid communication with the P6 oil port of the C0 electromagnetic valve 11, and the pressure reducing valve 12 can reduce the oil pressure of a main oil way so that the C0 electromagnetic valve 11 is suitable for design requirements.
The oil drain back pressure valve 13 is an overflow valve, the set pressure is 1bar, namely when the oil pressure of an oil inlet exceeds 1bar, an inlet of the oil drain back pressure valve 13 is communicated with the oil pan 1, and oil drain is started. The P8 port of the oil drain back pressure valve 13 is respectively communicated with the T8 port of the pressure reducing valve 12 and the T5 port of the C0 pressure control slide valve 9, so that when the C0 electromagnetic valve 11 does not work, as shown in FIG. 5, the T5 port is communicated with the A4 port through a valve core, the A4 port is communicated with the C0 clutch, and at the moment, the oil in the clutch oil duct can be ensured to be incompletely emptied due to the existence of the oil drain back pressure valve 13. For the oil flushing passage and the piston cavity of the clutch, the whole space is larger, and if the oil flushing passage and the piston cavity are emptied, the clutch is combined until the next oil flushing is needed, so that a long time is needed, and the power switching of the gearbox is not facilitated. However, the arrangement of the oil drain back pressure valve 13 can ensure that the oil duct is not emptied after the last use, and ensure that the clutch used next time can react quickly.
Wherein the main oil pressure solenoid valve 6 and the C0 solenoid valve 11 are a two-position three-way proportional solenoid valve, and the main oil passage pressure control spool valve 7, the C0 pressure control spool valve 9 and the pressure reducing valve 12 are pressure control spool valves; the drain back pressure valve 13 and the lubrication back pressure valve 8 are relief valves. The mechanical pump power source is a gearbox input shaft; the power source of the electronic pump is a storage battery and is controlled by a control system; the hydraulic actuating element in the hydraulic system is a C0 clutch; the oil cooling and lubrication of the hybrid power module is provided by a lubrication oil way of the hydraulic system; the oil pan 1 is a cavity for fluid oil, and provides an independent fluid source for a hydraulic system of the mixing module.
The hydraulic control system for the hybrid hydraulic automatic gearbox provided by the invention comprises different operation modes or states, and mainly realizes the different modes by the hydraulic system, wherein the specific modes are as follows:
vehicle launch uses motor start engine mode: at this time, the motor and the electronic pump 4 are driven by the storage battery to work, the engine is not moved, and the mechanical pump 3 is not operated. The electronic pump 4 pumps oil from the oil pan 1 into the hydraulic system module, and due to the restriction of the electronic pump 4, the main oil line oil pressure is small, and the main oil line pressure control spool 7 may not be able to move downward against the spring force. In order to ensure lubrication and cooling of the mixing module, the main oil pressure electromagnetic valve 6 is regulated through an electric control system, as shown in fig. 4, so that the main oil pressure electromagnetic valve 6 outputs oil pressure, the main oil way pressure control slide valve 7 is pushed to move downwards, and the P1 port is communicated with the B port oil. Because the mode does not need a C0 clutch to be slipped and ground, the lamination is directly pressed. The electric control system directly gives the maximum current command to the C0 electromagnetic valve 11, and as shown in FIG. 6, the P4 port of the C0 pressure control slide valve 9 is communicated with the A4 port to charge and compress the C0 clutch. After the C0 clutch is tightly pressed, the motor is connected with the power of the engine flywheel, the motor starts to drive the engine flywheel to rotate from 0 to idle speed, at the moment, the electronic pump 4 is closed, and the mechanical pump 3 of the hybrid power module starts to rotate to supply oil to the hydraulic module.
Hybrid driving mode: when the vehicle has a certain speed, the battery is insufficient, the engine is needed to intervene at the moment, because the vehicle is running, the mechanical pump 3 of the hydraulic gearbox body is running to provide system oil pressure for the body, and the motor is needed to be used for improving the rotating speed of the engine at the moment so as to achieve the running speed at the moment, so that a driver can not feel the change of the speed, and the driving comfort is ensured. In order to smoothly switch, the C0 clutch is required to be firstly subjected to sliding grinding and then combined with pressing, power is stably transmitted in the sliding grinding process, the rotating speed of the engine is driven to slowly rise, the C0 clutch is pressed after the rotating speed rises to the target rotating speed, the hybrid power driving mode is adopted, the C0 clutch is disconnected after the smooth switching, namely the oil flushing oil way is subjected to pressure relief, the engine is used as power to drive the vehicle to drive, and the motor is turned off. This process requires the hydraulic system of the hybrid module to participate, ensuring the slipping of the C0 clutch and the cooling and lubrication of the hybrid module, as described above: the electronic pump 4 is started to establish the oil pressure of the hybrid module, in order to ensure the smooth grinding of the C0 clutch, an electric control system is required to control the electric current of the C0 electromagnetic valve 11 to slowly change, at the moment, the C0 pressure control slide valve 9 slowly moves downwards, the P4 is communicated with the port A4, the pilot control oil pressure P (X4) linearly changes, so that the linear change of the P (A4) gradually increases, the smooth grinding of the C0 clutch in the earlier stage is ensured, the torque transmission drives the engine flywheel to rotate so as to gradually increase the engine speed, and after the engine speed is increased to an idle point, the electronic pump 4 is closed, the mechanical pump 3 of the hybrid module is started to provide the oil pressure of the hydraulic system of the hybrid module.
Engine running mode: the engine rotates, the mechanical pump 3 of the mixing module rotates to provide the oil pressure of the hydraulic system of the mixing module, no power switching is needed at this time, i.e. the C0 clutch is not combined, and the hydraulic system mainly provides the lubrication and cooling of the bearing of the mixing module.
Pure electric mode: at this time, the motor directly drives the hydraulic gearbox body to rotate to provide power, the hydraulic system of the mixing module does not need to work, and at this time, the electronic pump 4 and the mechanical pump 3 do not work.
The above is only for illustrating the technical idea of the present invention, and the protection scope of the present invention is not limited by this, and any modification made on the basis of the technical scheme according to the technical idea of the present invention falls within the protection scope of the claims of the present invention.
Claims (9)
1. A hydraulic control system for a hybrid hydraulic automatic transmission, characterized by comprising an oil pan (1), an oil filter-coarse (2), a mechanical pump (3), an electronic pump (4), a main oil pressure solenoid valve (6), a main oil line pressure control slide valve (7), a lubrication back pressure valve (8), a C0 pressure control slide valve (9), a C0 solenoid valve (11), a pressure reducing valve (12) and a drainage back pressure valve (13);
the oil pan (1) is communicated with an oil inlet of the oil filter-coarse (2), the mechanical pump (3) and the electronic pump (4) are connected in parallel, oil inlets of the mechanical pump (3) and the electronic pump (4) are communicated with an oil outlet of the oil filter-coarse (2), and oil outlets of the mechanical pump (3) and the electronic pump (4) are communicated with a main oil way pressure control slide valve (7); the main oil way pressure control slide valve (7) is respectively connected with the main oil pressure electromagnetic valve (6), the lubrication back pressure valve (8), the C0 pressure control slide valve (9) and the pressure reducing valve (12); the lubrication back pressure valve (8) is connected with a lubrication oil duct of the mixing module; the C0 pressure control slide valve (9) is respectively connected with a C0 pressure measuring point (14), a C0 electromagnetic valve (11), a pressure reducing valve (12), a draining back pressure valve (13) and a main oil pressure electromagnetic valve (6); the C0 electromagnetic valve (11) is connected with the pressure reducing valve (12); the pressure reducing valve (12) is connected with the oil drainage back pressure valve (13);
the main oil way pressure control slide valve (7) is provided with pilot control oil ways X1 and X2, the port A2 of the main oil pressure solenoid valve (6) is in fluid connection with the port X1, the port A1 of the main oil way pressure control slide valve (7) is respectively connected with the pilot control oil way X2, the port P2 of the main oil pressure solenoid valve (6) and the main oil way m, the port B of the main oil way pressure control slide valve (7) is communicated with the lubricating oil way, and the port A1 of the main oil way pressure control slide valve (7) is respectively communicated with the port P4 of the C0 pressure control slide valve (9) and the port P7 of the pressure reducing valve (12) through the main oil way m.
2. A hydraulic control system for a hybrid automatic transmission according to claim 1, characterized in that an accumulator (10) is also provided, the accumulator (10) being connected to the C0 pressure control spool (9) and the C0 solenoid valve (11), respectively.
3. A hydraulic control system for a hybrid hydraulic automatic gearbox according to claim 1, characterised in that an oil filter-concentrate (5) is also provided, the oil inlet of the oil filter-concentrate (5) being in communication with the oil outlets of the mechanical pump (3) and the electronic pump (4), the oil outlet of the oil filter-concentrate (5) being in communication with the main oil circuit pressure control slide valve (7).
4. A hydraulic control system for a hybrid hydraulic automatic gearbox according to claim 1, characterised in that the oil outlet of the electronic pump (4) is also provided with a non-return valve.
5. A hydraulic control system for a hybrid automatic transmission according to claim 1, characterized in that the main oil pressure solenoid valve (6) and the C0 solenoid valve (11) are both proportional solenoid valves.
6. A hydraulic control system for a hybrid automatic transmission according to claim 1, characterized in that the main oil pressure solenoid valve (6) and the C0 solenoid valve (11) are two-position three-way proportional solenoid valves.
7. A hydraulic control system for a hybrid automatic transmission according to claim 2, characterized in that an orifice is provided between the outlet of the C0 pressure control spool (9) and the inlet of the accumulator (10).
8. A hydraulic control system for a hybrid automatic transmission according to claim 2, characterized in that the pilot control X4 of the C0 pressure control spool (9) is in fluid communication with the A6 port of the C0 solenoid valve (11) and the P5 port of the accumulator (10); an A7 oil port of the pressure reducing valve (12) is in fluid communication with a P6 oil port of the C0 electromagnetic valve (11).
9. A vehicle comprising a hydraulic control system for a hybrid hydraulic automatic transmission according to any one of claims 1-8.
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