CN115182990A - Hydraulic control system for hybrid power hydraulic automatic gearbox - Google Patents
Hydraulic control system for hybrid power hydraulic automatic gearbox Download PDFInfo
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- CN115182990A CN115182990A CN202210631335.8A CN202210631335A CN115182990A CN 115182990 A CN115182990 A CN 115182990A CN 202210631335 A CN202210631335 A CN 202210631335A CN 115182990 A CN115182990 A CN 115182990A
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- 239000003921 oil Substances 0.000 claims abstract description 312
- 230000001050 lubricating effect Effects 0.000 claims abstract description 15
- 239000010687 lubricating oil Substances 0.000 claims abstract description 11
- 238000002156 mixing Methods 0.000 claims abstract description 5
- 239000012530 fluid Substances 0.000 claims description 22
- 238000004891 communication Methods 0.000 claims description 10
- 230000005540 biological transmission Effects 0.000 claims description 9
- 239000013589 supplement Substances 0.000 abstract description 2
- 238000013461 design Methods 0.000 description 10
- 238000000034 method Methods 0.000 description 8
- 101150006573 PAN1 gene Proteins 0.000 description 7
- 238000001914 filtration Methods 0.000 description 7
- 239000012535 impurity Substances 0.000 description 7
- 238000010586 diagram Methods 0.000 description 6
- 238000011010 flushing procedure Methods 0.000 description 6
- 238000005461 lubrication Methods 0.000 description 6
- 238000001816 cooling Methods 0.000 description 5
- 239000010729 system oil Substances 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000003749 cleanliness Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 238000000227 grinding Methods 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 238000009530 blood pressure measurement Methods 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000009977 dual effect 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
- 239000007788 liquid Substances 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
- 230000036632 reaction speed Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0402—Cleaning of lubricants, e.g. filters or magnets
- F16H57/0404—Lubricant filters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—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
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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
- F16H61/0031—Supply of control fluid; Pumps therefore using auxiliary pumps, e.g. pump driven by a different power source than the engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/2807—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
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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
- F16H2061/0037—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
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- 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 power hydraulic automatic gearbox, and belongs to the technical field of hydraulic control. The system comprises an oil sump, wherein an oil filter-coarse oil outlet is connected to the oil sump, a mechanical pump and an electronic pump which are connected in parallel are connected to the oil outlet of the oil filter-coarse oil outlet, 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 lubricating back pressure valve, a C0 pressure control slide valve and a pressure reducing valve; the lubricating back pressure valve is connected with a lubricating oil channel 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, an oil drainage 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 drainage back pressure valve. The system is relatively independent, the capacity of other systems is not required to be increased to supplement extra load generated by the hybrid power module, the resources of other systems of a vehicle are not obviously consumed, the main oil pressure is adjustable, and the system is easily adapted to more types of gearboxes.
Description
Technical Field
The invention belongs to the technical field of hydraulic control, and particularly relates to a hydraulic control system for a hybrid power hydraulic automatic gearbox.
Background
Under the increasingly severe global climate conditions and the increasingly strict new carbon emission regulations, the development of new energy automobiles becomes the mainstream trend. The requirements for long distance running and torque of commercial vehicles are large, and the market is also cost-sensitive. Therefore, the hybrid power assembly is the mainstream trend at present, the original vehicle platform can be changed, and the development cost and the risk are reduced. And meanwhile, the requirements of higher power, lower fuel consumption and lower emission in daily running are met.
The hybrid transmission is mainly developed by the structure and the arrangement of a hydraulic system, but as a hybrid power assembly of the hydraulic automatic transmission has multiple driving modes and additional lubricating and cooling requirements, additional hydraulic pumps of a vehicle in an electric power mode or a mode that a motor starts an engine to drive are mutually interfered, and the burden of other systems is increased; in addition, the oil pressure of the main oil circuit of the hydraulic system cannot be adjusted, and the hydraulic system cannot be compatible with oil pumps with different performances and cannot meet different pressure requirements of the C0 clutch under 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 additional hydraulic pumps interfere with each other in a pure electric mode or a mode of running a motor-started engine, the oil pressure of a main oil circuit of a hydraulic system cannot be adjusted, oil pumps with different performances cannot be compatible, and the C0 clutch cannot meet different pressure requirements in different vehicle modes.
In order to achieve the purpose, the invention adopts the following technical scheme to realize the purpose:
the invention discloses a hydraulic control system for a hybrid power hydraulic automatic gearbox, which comprises an oil pan, an oil filter, a coarse oil pump, a mechanical pump, an electronic pump, a main oil pressure electromagnetic valve, a main oil way pressure control slide valve, a lubricating back pressure valve, a C0 pressure control slide valve, a C0 electromagnetic valve, a pressure reducing valve and an oil drainage back pressure valve, wherein the oil filter is arranged on the oil pan;
the oil pan is communicated with an oil filter-thick 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 an oil filter-thick oil outlet, and the oil outlets of the mechanical pump and the electronic pump are communicated 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 lubricating back pressure valve, a C0 pressure control slide valve and a pressure reducing valve; the lubricating back pressure valve is connected with a lubricating oil channel 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, an oil drainage 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 drainage back pressure valve.
Preferably, an accumulator is further provided, and the accumulator is respectively connected with the C0 pressure control spool valve and the C0 solenoid valve.
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 pressure control slide valve is provided with pilot control oil paths X1 and X2, X1 is in fluid connection with an A2 port of the main oil pressure solenoid valve, a branch oil path of the A1 port of the main oil pressure control slide valve respectively enters a pilot control oil port X2, a P2 port of the main oil pressure solenoid valve and a main oil path m, a B port of the main oil pressure control slide valve is communicated with a lubricating oil path, and the A1 port of the main oil pressure control slide valve is respectively communicated with a P4 port of the C0 pressure control slide valve and a P7 port of the reducing valve through the main oil path m.
Preferably, the oil outlet of the electronic pump is further 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 proportional solenoid valves.
Preferably, an orifice is provided between the outlet of the C0 pressure control spool valve 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 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 which comprises the hydraulic control system for the hybrid power hydraulic automatic gearbox.
Compared with the prior art, the invention has the following beneficial effects:
according to the hydraulic control system for the hybrid power hydraulic automatic gearbox, the oil pan provides a fluid source for the system, then the fluid is filtered through the oil filter and coarse filtering, the hydraulic valve plate is prevented from being clamped and blocked by impurities, and the filtered fluid enters the mechanical pump and the electric pump and becomes fluid with pressure. The parallel design of the mechanical pump and the electric pump is used as an independent system, the electric pump can share the working load for the mechanical pump when needed, the burden of other systems is not increased, the dual pump system is beneficial to reducing the size and the weight of the required mechanical pump, the running of the system in a complete electric mode can be met, and the problem of hybrid multi-mode running is effectively solved. In order to be compatible with two oil pumps with different performances, a main oil pressure electromagnetic valve is connected in parallel on the basis of a main oil way pressure control slide valve, so that the main oil pressure can be adjusted, the oil pumps with different performances are compatible, and different pressure requirements of a C0 clutch under different vehicle modes and the use working conditions of more hybrid power gearboxes are met. The arrangement of the lubricating back pressure valve and the oil drainage back pressure valve in the oil drainage oil path can ensure that oil does not flow back, and meanwhile, the oil path of the execution element is not emptied when the oil path does not work, so that the reaction speed of the whole hydraulic system is ensured to be more sensitive. The connection of the main oil pressure solenoid valve with the C0 pressure control spool valve can provide oil with a stable oil pressure for the pressure control valve. The setting of relief pressure valve can reduce too big main oil circuit oil pressure to the setting value to guarantee that control oil circuit oil pressure meets the demands, in order to reach more accurate oil pressure control. The system is relatively independent, the capacity of other systems is not increased to supplement extra workload generated by the hybrid module, the resources of other systems of a vehicle are not required to be obviously consumed, 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 the system is easily adapted to more types of gearboxes.
Further, an energy accumulator is arranged on an oil path of the hydraulic actuating element, so that the effects of stable rising and rapid falling of oil pressure can be achieved, the work of the actuating element is facilitated, and the gear shifting experience is better.
Furthermore, the oil filter-essence can be matched with the oil filter-coarse in use, and on the basis that the oil filter-coarse filters larger impurity particles, finer impurities can be filtered, so that the situation that the valve core is clamped and blocked due to the fact that the fine impurities enter the hydraulic valve plate module is prevented, and the performance of the whole vehicle is influenced.
Drawings
FIG. 1 is a hydraulic schematic of the hydraulic control system of the present invention with the various hydraulic components 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 configuration of the main oil pressure solenoid valve and the main oil line pressure control spool valve in the hydraulic control system of the present invention;
FIG. 4 is a schematic structural diagram of the operating states of a main oil pressure solenoid valve and a main oil path pressure control spool valve in the hydraulic control system of the present invention;
FIG. 5 is a schematic diagram of the configuration of the C0 solenoid valve, C0 pressure control spool valve and accumulator in the hydraulic control system of the present invention;
fig. 6 is a schematic structural diagram of the working states of a C0 solenoid valve, a C0 pressure control spool valve and an 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-fine; 6-main oil pressure solenoid valve; 7-main oil line pressure control slide valve; 8-lubricating a back pressure valve; a 9-C0 pressure control spool valve; a 10-C0 pressure control spool valve; 11-C0 solenoid valve; 12-a pressure relief valve; 13-oil drainage back pressure valve; 14-C0 pressure measurement point.
Detailed Description
In order to make the technical solutions of the present invention better understood, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be obtained by a person skilled in the art without making any creative effort based on the embodiments in the present invention, shall fall within the protection scope of the present invention.
It is noted that the terms "comprises" and "comprising," and 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, 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 the accompanying figures 1-6:
the invention provides a hydraulic control system for a hybrid power 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 lubricating 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.
Referring to fig. 1 and 2, the oil pan 1 provides a fluid source to provide separate oil for the hydraulic system circulation for the hybrid module, and can be used as an independent system without interfering with oil of other systems. The oil pan 1 is communicated with an oil inlet of an oil filter-coarse 2, and the oil filter-coarse 2 is placed between an oil inlet formed by the mechanical pump 3 and the electric pump 4 and an oil way of the oil pan 1 in a magnet mode, so that large impurities can be filtered for system oil, and the cleanliness of the system oil entering the oil pump is guaranteed. 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, an oil outlet of the oil filter-coarse 2 is communicated with oil inlets of the mechanical pump 3 and the electronic pump 4, when the mechanical pump 3 or the electronic pump 4 works, fluid oil in the oil pan 1 is sucked into the oil filter-coarse 2 for primary coarse filtration, and the fluid oil is changed into 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 case the engine is turned off and the hybrid module needs hydraulic oil. In order to prevent the high-pressure oil at the oil outlet of the mechanical pump 3 from flowing into the electronic pump 4 when the mechanical pump works, the oil outlet of the electronic pump 4 is also provided with a one-way valve, and the one-way valve only allows the fluid to flow from the oil inlet a to the oil outlet b of the electronic pump 4. The mechanical pump 3 is mechanically connected to the engine via the input shaft, and cannot move in the reverse direction by the oil pressure of the electronic pump 4, so that a check valve is not required. The oil outlets of the mechanical pump 3 and the electronic pump 4 are communicated with an oil filter-essence 5, the oil filter-essence 5 is externally arranged and can be replaced periodically, and high-pressure oil at the outlet of the mechanical pump 3 or the electronic pump 4 can pass through the oil filter-essence 5 to be filtered and then enters the hydraulic valve plate. The hydraulic valve plate is a precision matching piece, very fine oil impurities can cause clamping stagnation of a valve core and affect the performance of the gearbox, the oil filter-fine 5 is used for secondary filtering on the basis that the oil filter-coarse 2 filters out larger impurities, and the two-stage filtering (coarse filtering and fine filtering) can better ensure the cleanliness of oil, so that the filtering 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-fine 5 is communicated with the P1 oil inlet of the main oil circuit pressure control slide valve 7, the main oil pressure electromagnetic valve 6 and the main oil circuit pressure control slide valve 7 control and adjust the main oil circuit oil pressure (namely the A1 port oil pressure of the main oil circuit pressure control slide valve 7) through the common action, the combined adjustment can be controlled by a controller, the variable main oil circuit oil pressure is realized, and different use scenes are adapted. The main oil path pressure control slide valve 7 is provided with two pilot control oil paths X1 and X2, X2 is feedback oil pressure of an A1 port, X1 is in fluid connection with an A2 port of a main oil pressure electromagnetic valve 6 and is pilot control oil pressure of the main oil path pressure control slide valve 7, the main oil pressure electromagnetic valve 6 is a proportional electromagnetic valve, and the size of the oil pressure of the A2 port can be controlled through an electric control system. As shown in fig. 3 and 4: the port A1 of the main oil line pressure control spool 7 is divided into three oil lines which respectively enter the pilot control oil port X2, the port P2 of the main oil pressure solenoid valve 6 and the main oil line m (as shown in fig. 2), the port B of the main oil line pressure control spool 7 leads to the lubricating oil line, the main oil pressure solenoid valve 6 is directly arranged right above the main oil line pressure control spool 7 in structure, and the oil outlet A2 of the main oil pressure solenoid valve 6 directly acts on the upper end surface of the main oil line pressure control spool 7, namely the pilot control oil line X1 of the main oil line pressure control spool 7. When pressure oil from an oil pump (i.e., the mechanical pump 3 or the electronic pump 4) reaches the port P1 of the main oil path pressure control spool 7, if the oil pressure is smaller than a designed value P0, the spool is stationary, and the state is as shown in fig. 3, i.e., the oil pressure at the port A1 is equal to the oil pressure at the port P1 and equal to the oil pressure at the pilot control port X2, the main oil pressure solenoid valve 6 is closed, and P (X2) × S is smaller than or equal to F (spring force), the spool is stationary, and no fluid flows out from the port B, i.e., the lubricating oil path. When the pressure of the port P1 of the main oil circuit pressure control slide valve 7 is larger than a designed value P0, the oil pressure of the port A1 of the main oil circuit pressure control slide valve 7 is equal to the oil pressure of the port X2, at the moment, P (X2) S is larger than F (spring force), the valve core is forced to move downwards, the port A1 is communicated with the port B, oil drainage to the lubricating oil channel is started, when the liquid flow of fluid oil from the oil pump is increased, the oil pressure of the port P1 is increased, so that the valve core continues to move downwards, the port A1 is communicated with the port B and the port T2 to further drain oil (as shown in figure 4), and the oil pressure of the port A1 is further reduced to reach the designed 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 is not communicated with the port T2, and the position of the valve core can be dynamically adjusted all the time to keep the oil pressure of the port A1 never to exceed a designed value p0. However, for a hydraulic system of a hybrid module, the capacity of the generally equipped electronic pump 4 is weak, the flow rate and the oil pressure are low, and the design value p0 may not be reached. If the valve core is not in the moving state, the port A1 has oil pressure, but the port B of the lubricating oil path has no fluid, so that the normal work of the mixing module is not facilitated. At this time, the main oil pressure solenoid valve 6 may be opened, and the main oil pressure solenoid valve 6 may regulate the outlet oil pressure to change linearly according to the solenoid valve current, that is, the X1 pilot control oil pressure changes linearly, so as to control the oil pressure of the port A1 through the electric control system. The valve core can move downwards when the value of p (X2) + p (X1) } S is larger than F (spring force), the port B is communicated with the port A1, the oil pressure of the port A1 can be adjusted and changed due to the linear change of the oil pressure of the port X1, and a design value p0 is not a fixed value, so that the flexible design can meet the use working conditions of more hybrid power gearboxes.
The oil inlet P3 of the lubricating back pressure valve 8 is in fluid communication with the port B of the main oil way pressure control slide valve 7 and a lubricating oil channel of the mixing module, the lubricating back pressure valve 8 is an overflow valve, the oil pressure of the main oil inlet P3 can be guaranteed to be stable at a design value, when the design value is exceeded, the main oil inlet P3 of the lubricating back pressure valve 8 is communicated with the main oil drainage port T4, the oil pressure is reduced through oil drainage, when the design value is reduced, the spring force pushes the valve core to move so that the oil port is disconnected, namely, the lubricating oil way is stabilized under certain pressure.
The port A1 of the main oil path pressure control spool 7 communicates with the port P4 of the C0 pressure control spool 9 and the port P7 of the pressure reducing valve 12, respectively, through a main oil path m (see fig. 2), and supplies a stable main oil pressure to the actuators of the subsequent hydraulic system.
Fig. 5 and 6 are schematic diagrams showing the structures of the C0 solenoid valve 11, the C0 pressure control spool 9, and the accumulator 10, and adopt a similar structure to that of the main oil passage control valve. The C0 electromagnetic valve 11 is directly arranged on 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 port A6 of the C0 electromagnetic valve 11 and the port P5 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 can be controlled to be changed proportionally by the electronic control system, so that the oil pressure of the pilot control X4 of the C0 pressure control spool 9 is influenced to be changed proportionally. The C0 pressure control spool 9 linearly changes the oil pressure at the A4 port from 0 to a set value by the combined action of the pilot control X4, the feedback control X3, and the spring force. Energy storageThe device 10 can stably control the oil pressure X4 of the C0 pressure control slide valve 9, so that the pressure is stably and continuously increased, and simultaneously, the maximum value can be quickly changed into 0, and the linear control of the clutch pressure of the hydraulic actuator C0 is realized. When the C0 solenoid valve 11 receives the output oil pressure of the current signal solenoid valve, that is, the oil pressure of the pilot control port 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 value of the oil pressure at port A4) when p (pilot X4) changes linearly, p (port A4) also changes linearly. The diameter is set between the oil pressure at the X4 outlet of the C0 pressure control slide valve 9 and the oil path at the inlet of the accumulator 10
The throttling hole can avoid the gear shifting impact caused by too fast oil pressure change of the port A4 and too fast oil flushing of the clutch; meanwhile, in the oil flushing process, 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 will be quickly drained to 0, but at this time, due to the existence of the accumulator 10, the oil pressure of the port X4 will not be quickly changed to 0, and the pressure oil stored in the accumulator 10 will be slowly released through the orifice, so that the shifting impact at the moment of clutch switching can be reduced, and the clutch can be released relatively slowly.
The A7 port of the pressure reducing valve 12 is in fluid communication with the P6 port of the C0 solenoid valve 11, and the pressure reducing valve 12 can reduce the oil pressure of the main oil path, so that the C0 solenoid valve 11 is suitable for the design requirements.
The oil drainage back pressure valve 13 is an overflow valve, the set pressure is 1bar, namely when the oil pressure of an oil inlet exceeds 1bar, the inlet of the oil drainage back pressure valve 13 is communicated with the oil pan 1, and oil drainage is started. The P8 port of the oil drainage 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 figure 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, because of the existence of the oil drainage back pressure valve 13, the oil in an oil passage of the clutch can be ensured to be not completely drained. For the oil flushing channel and the piston cavity of the clutch, the whole space is large, if the oil flushing channel and the piston cavity are emptied, oil flushing is needed until the next time, and the clutch is combined, a long time is needed, so that power switching of the gearbox is not facilitated. But the oil drainage back pressure valve 13 can ensure that the oil duct is not emptied after the last use, and the next use of the clutch can quickly react.
Wherein, the main oil pressure solenoid valve 6 and the C0 solenoid valve 11 are two-position three-way proportional solenoid valves, and the main oil path 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 the control system; the hydraulic actuator in the hydraulic system is a C0 clutch; oil cooling and lubrication of the hybrid power module are 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 hybrid module.
The invention provides a hydraulic control system for a hybrid power hydraulic automatic gearbox, which comprises different operation modes or states, wherein the different modes are realized mainly by a hydraulic system, and the specific modes are as follows:
the vehicle starts to use the motor to start the 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 does not work. The electronic pump 4 pumps oil from the oil sump 1 into the hydraulic system module, and due to the restriction of the electronic pump 4, the main line oil pressure is small, and it may not be possible to move the main line pressure control spool 7 downward against the spring force. In order to ensure the lubrication and cooling of the hybrid module, the main oil pressure solenoid valve 6 is adjusted by the electronic control system, as shown in fig. 4, so that the main oil pressure solenoid valve 6 outputs oil pressure to push the main oil pressure control slide valve 7 to move downwards, and the communication between the port P1 and the port B is ensured. Because C0 clutch sliding friction is not needed in the mode, the clutch is directly pressed and attached. The electronic control system directly gives a maximum current instruction to the C0 electromagnetic valve 11, as shown in fig. 6, the P4 port of the C0 pressure control slide valve 9 is communicated with the A4 port, and oil is filled and compressed for the C0 clutch. After the C0 clutch is pressed, the motor is in power connection with the engine flywheel, the motor starts to rotate from 0 to drive the engine flywheel to rotate to an idle speed, the electronic pump 4 is closed at the moment, 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 car has certain speed of a motor vehicle, the battery power is not enough, needs the engine to intervene this moment, because is going, the mechanical pump 3 of hydraulic transmission body is moving and is providing system oil pressure for the body, needs to use the motor to promote the engine speed this moment to reach the speed of a motor vehicle of going this moment, the driver can not experience the change of the speed of a motor vehicle, guarantees the travelling comfort of driving. In order to switch smoothly, the C0 clutch is required to be firstly subjected to sliding grinding and then combined to be pressed, power is stably transmitted in the sliding grinding process to drive the rotating speed of the engine to slowly rise, the C0 clutch is pressed to be pressed after the rotating speed rises to a target rotating speed, a hybrid power running mode is adopted, the C0 clutch is disconnected after the switching is stable, namely an oil flushing oil path is used for pressure relief, the engine is used as power to drive the vehicle to run, and the motor is turned off. This process requires the participation of the hydraulic system of the hybrid module, ensuring the slip 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 sliding abrasion of the C0 clutch, an electric control system is required to control the linear slow change of the current of a C0 electromagnetic valve 11, at the moment, a C0 pressure control slide valve 9 slowly moves downwards, a port P4 is communicated with a port A4, and a pilot control oil pressure P (X4) linearly changes, so that the linear change of the P (A4) is gradually increased, the stable sliding abrasion of the C0 clutch in the early stage is ensured, the torque transmission drives an engine flywheel to rotate so that the rotating speed of the engine is gradually increased, after the rotating speed of the engine 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.
An engine running mode: the engine rotates, the hybrid module mechanical pump 3 rotates to provide oil pressure for a hybrid module hydraulic system, power switching is not needed at the moment, namely, a C0 clutch is not combined, and the hydraulic system mainly provides bearing lubrication and cooling for the hybrid module.
Pure electric mode: at this moment, the motor directly drives the hydraulic transmission body to rotate to provide power, the hydraulic system of the hybrid module does not need to work, and the electronic oil pump 4 and the mechanical pump 3 do not work at this moment.
The above contents are only for illustrating the technical idea of the present invention, and the protection scope of the present invention should not be limited thereby, and any modification made on the basis of the technical idea proposed by the present invention falls within the protection scope of the claims of the present invention.
Claims (10)
1. A hydraulic control system for a hybrid hydraulic automatic gearbox is characterized by comprising an oil pan (1), an oil filter-coarse (2), a mechanical pump (3), an electronic pump (4), a main oil pressure electromagnetic valve (6), a main oil circuit pressure control slide valve (7), a lubricating back pressure valve (8), a C0 pressure control slide valve (9), a C0 electromagnetic valve (11), a pressure reducing valve (12) and an oil 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) is connected with the electronic pump (4) 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 the main oil way pressure control slide valve (7); the main oil circuit pressure control slide valve (7) is respectively connected with a main oil pressure electromagnetic valve (6), a lubricating back pressure valve (8), a C0 pressure control slide valve (9) and a reducing valve (12); the lubricating back pressure valve (8) is connected with a lubricating oil channel 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), an oil drainage 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 an oil drainage back pressure valve (13).
2. A hydraulic control system for a hybrid automatic hydrodynamic gearbox according to claim 1, characterized in that an accumulator (10) is provided, the accumulator (10) being connected to the C0 pressure control slide valve (9) and the C0 solenoid valve (11), respectively.
3. The hydraulic control system for a hybrid hydraulic automatic gearbox according to claim 1, characterized in that an oil filter-strainer (5) is further provided, the oil inlet of the oil filter-strainer (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-strainer (5) being in communication with the main circuit pressure control slide valve (7).
4. The hydraulic control system for a hybrid hydraulic automatic transmission according to claim 1, wherein the main oil path pressure control spool (7) has pilot oil paths X1 and X2, X1 is fluidly connected to port A2 of the main oil pressure solenoid valve (6), port A1 of the main oil path pressure control spool (7) is branched into a pilot oil port X2, port P2 of the main oil pressure solenoid valve (6), and a main oil path m, port B of the main oil path pressure control spool (7) is connected to a lubricating oil path, and port A1 of the main oil path pressure control spool (7) is connected to port P4 of the C0 pressure control spool (9) and port P7 of the pressure reducing valve (12) through the main oil path m.
5. A hydraulic control system for a hybrid automatic hydrodynamic gearbox according to claim 1, characterized in that the oil outlet of said electronic pump (4) is also provided with a non-return valve.
6. The hydraulic control system for a hybrid automatic hydrodynamic transmission, according to claim 1, characterized in that the main oil pressure solenoid valve (6) and the C0 solenoid valve (11) are proportional solenoid valves.
7. The hydraulic control system for a hybrid automatic hydrodynamic gearbox according to claim 1, characterized in that the main oil pressure solenoid (6) and the C0 solenoid (11) are two-position three-way proportional solenoids.
8. A hydraulic control system for a hybrid automatic hydrodynamic gearbox according to claim 2, characterized in that an orifice is provided between the outlet of the C0 pressure control slide valve (9) and the inlet of the accumulator (10).
9. The hydraulic control system for a hybrid hydraulic 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 port A6 of the C0 solenoid valve (11) and the port P5 of the accumulator (10); the A7 port of the pressure reducing valve (12) is in fluid communication with the P6 port of the C0 electromagnetic valve (11).
10. A vehicle comprising a hydraulic control system for a hybrid automatic hydrodynamic transmission according to any one of claims 1 to 9.
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