CN116498746B - Control method of gearbox electrohydraulic control system - Google Patents
Control method of gearbox electrohydraulic control system Download PDFInfo
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- CN116498746B CN116498746B CN202310513162.4A CN202310513162A CN116498746B CN 116498746 B CN116498746 B CN 116498746B CN 202310513162 A CN202310513162 A CN 202310513162A CN 116498746 B CN116498746 B CN 116498746B
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- 238000000034 method Methods 0.000 title claims abstract description 30
- 238000005461 lubrication Methods 0.000 claims abstract description 145
- 239000003921 oil Substances 0.000 claims description 428
- 230000005540 biological transmission Effects 0.000 claims description 21
- 230000001050 lubricating effect Effects 0.000 claims description 20
- 230000001105 regulatory effect Effects 0.000 claims description 11
- 239000010687 lubricating oil Substances 0.000 claims description 3
- 238000001816 cooling Methods 0.000 abstract description 9
- 101150006573 PAN1 gene Proteins 0.000 description 6
- 239000000446 fuel Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 238000004891 communication Methods 0.000 description 4
- 230000001276 controlling effect Effects 0.000 description 2
- 230000006378 damage Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000012535 impurity Substances 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000035939 shock 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
- F16H61/38—Control of exclusively fluid gearing
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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
- F16H57/0409—Features relating to lubrication or cooling or heating characterised by the problem to increase efficiency, e.g. by reducing splash losses
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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
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0415—Air cooling or ventilation; Heat exchangers; Thermal insulations
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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
- F16H57/0436—Pumps
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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
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
- General Details Of Gearings (AREA)
Abstract
The invention provides a control method of an electrohydraulic control system of a gearbox, and the control method comprises the steps of obtaining an engine rotating speed signal; when the engine speed signal is greater than 0, acquiring a control loop flow demand and a lubrication loop flow demand; when the flow rate of the mechanical oil pump is larger than the flow rate requirement of the control loop and smaller than the flow rate requirement of the lubrication loop, the mechanical oil pump and the electronic oil pump work together, and the electronic oil pump directly supplies oil to the lubrication loop. According to the control method of the gearbox electrohydraulic control system, the electronic oil pump can be controlled to supply oil to the control system according to the flow of the mechanical oil pump, the flow requirement of the control loop and the flow requirement of the lubrication loop, so that the whole oil supply efficiency is improved, the electronic oil pump can directly supply oil to the lubrication loop, the electronic oil pump can conveniently provide enough cooling and lubrication flow, and the whole oil supply efficiency is further improved.
Description
Technical Field
The invention relates to the technical field of gearbox control systems, in particular to a control method of an electrohydraulic control system of a gearbox.
Background
The gearbox has been adopted by more and more vehicle enterprises because of the advantages of compact structure, good fuel economy, large torque transmission capability, good starting performance and gear shifting quality and the like.
The gearbox electrohydraulic control system can realize the combination and separation control, gear shifting control, electrohydraulic parking control and cooling and lubrication control of the gearbox. The existing new energy automobile gearbox electrohydraulic control system in industry is designed according to respective actual functional requirements and control logic in a targeted manner, and is mainly integrated by an oil supply system, a lubrication circuit, a control circuit and other electrohydraulic auxiliaries, wherein the oil supply system supplies oil to the whole gearbox electrohydraulic control system, cooling and lubrication control of the gearbox is realized through the lubrication circuit, and clutch combination and separation control, gear shifting control and electrohydraulic parking control in the gearbox are realized through the control circuit.
The existing double-clutch automatic gearbox or hybrid gearbox electrohydraulic control system is mainly supplied with oil by adopting a mechanical pump alone or by adopting a combination mode of a mechanical pump and an electronic pump, however, the existing double-clutch automatic gearbox or hybrid gearbox electrohydraulic control system is limited by the control mode of the existing gearbox control system, the working condition efficiency of the electronic oil pump is low, and even under severe working conditions, the electronic oil pump cannot provide enough lubrication and cooling flow, so that the oil supply efficiency of the whole gearbox is reduced.
Disclosure of Invention
In view of the above, the present invention is directed to a control method of an electro-hydraulic control system of a gearbox, so as to facilitate improving the oil supply efficiency of the whole gearbox.
In order to achieve the above purpose, the technical scheme of the invention is realized as follows:
A control method of a gearbox electrohydraulic control system, wherein the gearbox electrohydraulic control system is provided with a mechanical oil pump, an electronic oil pump, a main oil way, a control loop and a lubrication loop, wherein the control loop and the lubrication loop are connected with the main oil way, and the lubrication loop comprises a plurality of lubrication branches;
the control method comprises the following steps:
Acquiring an engine rotating speed signal;
When the engine speed signal is greater than 0, acquiring a control loop flow demand and a lubrication loop flow demand;
When the flow rate of the mechanical oil pump is larger than the flow rate requirement of the control loop and smaller than the flow rate requirement of the lubrication loop, the mechanical oil pump and the electronic oil pump work together, and the electronic oil pump directly supplies oil to the lubrication loop.
Further, the control method further includes:
when the engine speed signal is greater than 0, acquiring the flow demand of the lubrication circuit;
When the flow rate of the mechanical oil pump is larger than the flow rate requirement of the lubrication circuit, only the mechanical oil pump works, and the mechanical oil pump supplies oil to the control circuit and the lubrication circuit respectively through the main oil circuit.
Further, the control method further includes:
When the engine speed signal is greater than 0, acquiring a control loop flow demand;
When the flow rate of the mechanical oil pump is smaller than the flow rate requirement of the control loop, the mechanical oil pump and the electronic oil pump work together, and the electronic oil pump supplies oil to the main oil way.
Further, the control method further includes:
when the electronic oil pump supplies oil to the lubrication circuit directly, acquiring the current flow of the electronic oil pump;
When the current flow is not lower than a preset flow threshold, the electronic oil pump directly supplies oil to each lubrication branch;
and when the current flow is lower than the preset flow threshold, the electronic oil pump supplies oil to each lubricating branch through an oil cooler and/or a pressure filter.
Further, the control method further includes:
acquiring a vehicle gear shifting demand signal or a clutch flow demand signal when the engine speed signal is equal to 0;
When the vehicle gear-shifting demand signal is a gear-shifting demand signal or the clutch flow demand signal is a flow demand signal, the electronic oil pump supplies oil to the control loop and the lubrication loop through the main oil way respectively;
And when the vehicle gear-shifting demand signal is a gear-shifting-free demand signal or the clutch flow demand signal is a flow-free demand signal, the electronic oil pump directly supplies oil to the lubricating loop.
Further, the lubrication circuit comprises at least one of a first lubrication branch for lubricating the bearing and/or the gear, and a second lubrication branch for lubricating the clutch;
the control loop includes at least one of a clutch control leg, a shift control leg.
Further, the oil outlet of the electronic oil pump is connected in series with a first control valve element, the first control valve element is provided with a working position for supplying oil to the main oil way and a working position for supplying oil to a second control valve element, the lubricating circuit is connected in series with an oil cooler and a filter press which are sequentially arranged, and the second control valve element is provided with a working position for supplying oil to the oil cooler and a working position for directly supplying oil to the first lubricating branch and the second lubricating branch;
The main oil way is provided with a proportional pressure electromagnetic valve, the first lubrication branch is provided with a first mechanical reversing valve, the first mechanical reversing valve is controlled by the proportional pressure electromagnetic valve, and the gear shifting control branch is connected with the main oil way through the proportional pressure electromagnetic valve.
Further, the gear shifting control branch comprises at least a first gear shifting control branch and a second gear shifting control branch, a first gear shifting electromagnetic valve connected with the proportional pressure electromagnetic valve is arranged on the first gear shifting control branch, the first gear shifting control branch comprises a plurality of gear shifting units, and each gear shifting unit is connected with the first gear shifting electromagnetic valve through a second mechanical reversing valve;
the second gear shifting control branch circuit is provided with a second gear shifting electromagnetic valve connected with the proportional pressure electromagnetic valve;
The main oil way is provided with an electromagnetic reversing valve, and the second mechanical reversing valve and the second control valve are controlled by the electromagnetic reversing valve.
Further, two ends of the filter press are connected with filter press bypass valves in parallel; and/or the number of the groups of groups,
An oil cooler bypass valve connected in parallel between the oil inlet end of the oil cooler and the oil outlet end of the filter press is arranged in the lubricating loop; and/or the number of the groups of groups,
And a pressure limiting valve is connected in the lubrication circuit and is connected to an oil inlet of the mechanical oil pump.
Further, a third control valve element is arranged in the main oil path, and the third control valve element is provided with a working position for cutting off the oil supply to the lubrication circuit, a working position for supplying oil to the lubrication circuit and enabling part of lubricating oil to flow back to an oil inlet of the mechanical oil pump;
the third control valve is controlled by a main pressure regulating electromagnetic valve, and an outlet of the main pressure regulating electromagnetic valve is connected with a first energy accumulator.
Compared with the prior art, the invention has the following advantages:
according to the control method of the gearbox electrohydraulic control system, when the engine speed signal is greater than 0, the control loop flow demand and the lubrication loop flow demand are obtained, and the electronic oil pump is controlled to supply oil to the control system according to the flow of the mechanical oil pump, the control loop flow demand and the lubrication loop flow demand, so that the whole oil supply efficiency is improved, and the electronic oil pump is enabled to supply oil to the lubrication loop directly, so that the electronic oil pump is enabled to provide enough cooling lubrication flow, and the whole oil supply efficiency is further improved.
In addition, the mechanical oil pump works independently under the condition that the flow of the mechanical oil pump is larger than the flow requirement of the lubrication circuit, and the electronic oil pump does not need to be started, so that the energy consumption of the whole oil supply system is reduced, and the oil supply efficiency is improved. And when the flow rate of the mechanical oil pump is smaller than the flow rate requirement of the control loop, the mechanical oil pump and the electronic oil pump work together, so that the flow rate requirement of the whole control system can be conveniently met
In addition, when the current flow of the electronic oil pump is not lower than a preset flow threshold, the electronic oil pump is enabled to directly supply oil to each lubrication branch, and the pressure at the outlet of the electronic oil pump is reduced, so that the oil supply efficiency of the electronic oil pump is improved, and more lubrication and cooling flows can be provided.
Furthermore, the vehicle gear shifting demand signal is obtained when the engine speed is equal to 0, and when the vehicle gear shifting demand signal is the gear shifting demand, the electronic oil pump is respectively supplied to the control loop and the lubrication loop through the main oil way, when the vehicle does not have the gear shifting demand, the electronic oil pump is directly supplied to the lubrication loop, so that the gear shifting demand is met, the oil consumption is reduced, and the fuel economy of the whole vehicle is improved.
And the first control valve element and the second control valve element are arranged at the oil outlet of the electronic oil pump, so that the electronic oil pump can supply oil to the main oil way, the inlet of the oil cooler, the first lubrication branch and the second lubrication branch respectively according to requirements, the oil supply efficiency of the electronic oil pump is ensured, and the oil supply system is improved.
In addition, the proportional pressure electromagnetic valve is used for controlling the oil flow of the gear shifting control branch and the first mechanical reversing valve, so that the quantity of control valves is reduced, the control structure is simplified, the cost is reduced, the quantity of control channels of the TCU of the vehicle is reduced, and the arrangement is convenient. And the electromagnetic directional valve is used for controlling the second mechanical directional valve and the second control valve element, so that the number of the control valves is further reduced, and the control structure is simplified.
Secondly, through being equipped with oil cooler bypass valve and pressure limiting valve, can alleviate the pressure in the oil circuit, play the guard action to oil cooler and pressure filter, avoid causing harm to oil cooler and pressure filter because of the fluid pressure in the return circuit is too high. And the pressure limiting valve is communicated with the inlet of the mechanical oil pump, so that the backflow of part of oil can be realized, and the suction of the mechanical oil pump at a high rotating speed can be prevented while the oil path is protected.
Meanwhile, by the aid of the third control valve, oil supply of the main oil way to the lubricating circuit can be controlled, part of oil can flow back to the oil inlet of the mechanical oil pump, and suction of the mechanical oil pump at high rotating speed is avoided. And the pressure of the main pressure regulating electromagnetic valve can be stabilized by the first energy accumulator, so that the regulation of the main pressure regulating electromagnetic valve on the third control valve element is facilitated.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. In the drawings:
FIG. 1 is an exemplary flow chart of a control method of a transmission electro-hydraulic control system according to an embodiment of the present invention;
FIG. 2 is yet another exemplary flow chart of a control method of a transmission electro-hydraulic control system according to an embodiment of the present disclosure;
FIG. 3 is another exemplary flow chart of a control method of a transmission electro-hydraulic control system according to an embodiment of the present disclosure;
FIG. 4 is a schematic diagram of a transmission electro-hydraulic control system according to an embodiment of the present invention;
FIG. 5 is a schematic view of the flow path of oil when the mechanical oil pump and the electronic oil pump are operated together and the electronic oil pump is directly supplying oil to the lubrication circuit according to the embodiment of the present invention;
FIG. 6 is a schematic diagram of the flow path of oil when the mechanical oil pump and the electronic oil pump are operated together and the electronic oil pump is directly supplying oil to each lubrication branch according to the embodiment of the present invention;
FIG. 7 is a schematic diagram of the flow path of oil when the mechanical oil pump according to the embodiment of the invention works alone;
FIG. 8 is a schematic diagram of the flow path of oil when the mechanical oil pump according to the embodiment of the invention works alone and part of the oil returns;
FIG. 9 is a schematic diagram of the flow path of oil when the mechanical oil pump and the electronic oil pump are operated together and the electronic oil pump supplies oil to the main oil path according to the embodiment of the invention;
FIG. 10 is a schematic view of the flow path of oil when the electronic oil pump according to the embodiment of the invention is operated alone and supplying oil to the main oil passage;
fig. 11 is a schematic view of a flow path of oil when the electronic oil pump according to the embodiment of the invention works alone and supplies oil to the lubrication oil path.
Reference numerals illustrate:
1. A transmission oil pan; 2. a suction filter; 3. a mechanical oil pump; 4. an electronic oil pump; 5. a lubrication circuit; 6. a control loop; 7. a first control valve member; 8. a second control valve member; 9. a proportional pressure solenoid valve; 10. an electromagnetic reversing valve; 11. a main oil path; 12. a clutch; 13. a main pressure regulating solenoid valve; 14. a gear box; 15. a first accumulator; 16. a second accumulator; 17. a third control valve member;
51. A first lubrication branch; 52. a second lubrication branch; 501. an oil cooler; 502. a press filter; 503. a filter press bypass valve; 504. an oil cooler bypass valve; 505. a pressure limiting valve; 511. a first mechanical reversing valve; 512. a throttle valve; 521. a proportional flow solenoid valve;
61. A clutch control branch; 62. a shift control branch; 611. a clutch pressure control solenoid valve; 612. an oil pressure sensor; 613. a third accumulator; 621. a first shift control branch; 622. a first shift solenoid valve; 623. a second shift control branch; 624. a second shift solenoid valve; 625. a gear shift unit; 626. and a second mechanical reversing valve.
Detailed Description
It should be noted that, without conflict, the embodiments of the present invention and features of the embodiments may be combined with each other.
In the description of the present invention, it should be noted that, if terms indicating an orientation or positional relationship such as "upper", "lower", "inner", "outer", etc. are presented, they are based on the orientation or positional relationship shown in the drawings, only for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the apparatus or element to be referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like, if any, are also used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
Furthermore, in the description of the present invention, the terms "mounted," "connected," and "connected," are to be construed broadly, unless otherwise specifically defined. For example, the connection can be fixed connection, detachable connection or integrated connection; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art in combination with specific cases.
The invention will be described in detail below with reference to the drawings in connection with embodiments.
The embodiment relates to a control method of an electrohydraulic control system of a gearbox, as shown in fig. 1, the control method mainly comprises the following steps:
s1, acquiring an engine rotating speed signal;
S2, when the engine speed signal is greater than 0, acquiring a control loop flow demand and a lubrication loop flow demand;
s3, when the flow of the mechanical oil pump 3 is larger than the flow requirement of the control loop and smaller than the flow requirement of the lubrication loop, the mechanical oil pump 3 and the electronic oil pump 4 work together, and the electronic oil pump 4 supplies oil to the lubrication loop 5 directly.
It will be appreciated that when the engine speed signal is greater than 0, the vehicle is in the hybrid mode, and the engine is operated while driving the mechanical oil pump 3 to rotate. Through obtaining lubrication circuit flow demand and control circuit flow demand to when the flow of mechanical oil pump 3 is greater than control backward flow demand, be less than lubrication circuit flow demand, make electronic oil pump 4 direct to lubrication circuit 5 oil feed, be convenient for make electronic oil pump 4 provide sufficient cooling lubrication flow, and under the higher circumstances of main oil circuit 11 fluid pressure, through direct oil feed to lubrication circuit 5, can reduce the pressure of electronic oil pump 4 export, promote the work efficiency of electronic oil pump 4, and then promote whole case fuel feeding efficiency.
In the above steps, the engine speed may be detected by a TCU (automatic transmission control unit) of the vehicle, and the acquisition of the lubrication circuit flow rate demand, the control circuit flow rate demand, and the mechanical oil pump 3 flow rate may be acquired by the TCU. Of course, instead of using the TCU to detect the rotational speed of the engine, it may be detected using a rotational speed sensor commonly used in the art.
In addition, since the oil pumped by the mechanical oil pump 3 is related to the rotation speed of the engine and the magnitude of the main oil pressure when the mechanical oil pump 3 is in operation, as a preferred embodiment, as shown in fig. 2, after the engine rotation speed signal is obtained, when the engine rotation speed signal is greater than 0, the flow demand of the lubrication circuit is obtained, and when the flow of the mechanical oil pump 3 is greater than the flow demand of the lubrication circuit, only the mechanical oil pump 3 is operated, and the mechanical oil pump 3 supplies oil to the control circuit 6 and the lubrication circuit 5 through the main oil passage 11, respectively.
At this time, the oil of the mechanical oil pump 3 is enough to supply the whole control system, so that the electronic oil pump 4 is not required to be restarted, the energy consumption of the whole control system is further reduced, and the fuel economy and the oil supply efficiency of the whole vehicle are improved. Furthermore, the comparison of the flow rate of the mechanical oil pump 3 with the lubrication circuit flow rate demand and the control circuit flow rate demand described above can also be achieved by the TCU. Of course, instead of using a TCU, it may be implemented using a numerical comparator as is commonly used in the art.
Further, as further preferable, as shown in fig. 3, after the engine speed signal is acquired, when the engine speed signal is greater than 0, the control circuit flow rate demand is acquired, and when the flow rate of the mechanical oil pump 3 is smaller than the control circuit flow rate demand, the mechanical oil pump 3 and the electronic oil pump 4 are operated together, and the electronic oil pump 4 is caused to supply oil to the main oil passage 11. Thus, the flow requirement of the whole control system is conveniently met.
Also, as a preferred embodiment, as shown in fig. 3, when the electronic oil pump 4 directly supplies oil to the lubrication circuit 5, the current flow rate of the electronic oil pump 4 is obtained, when the current flow rate is not lower than a preset flow rate threshold value, the electronic oil pump 4 directly supplies oil to each lubrication branch, and when the current flow rate is lower than the preset flow rate threshold value, the electronic oil pump 4 supplies oil to each lubrication branch through the oil cooler 501 and the pressure filter 502.
It can be understood that when the current flow of the electronic oil pump 4 is not lower than the preset flow threshold, the electronic oil pump 4 is directly used for supplying oil to each lubrication branch, so that the oil pressure at the outlet of the electronic oil pump 4 can be reduced, the efficiency of the electronic oil pump 4 is further improved, and more cooling and lubrication flows are provided. It should be noted that, the preset flow threshold may be stored in the TCU, and the current flow of the electronic oil pump 4 may be obtained through the TCU, or may be obtained through a flowmeter commonly used in the prior art.
In addition, as a preferred embodiment, after the engine speed signal is obtained, when the engine speed signal is equal to 0, a vehicle gear shift demand signal is obtained, and when the vehicle gear shift demand signal is that there is a gear shift demand, the electronic oil pump 4 supplies oil to the control circuit 6 and the lubrication circuit 5 through the main oil passage 11, respectively. And when the vehicle gear shift demand signal is no gear shift demand, the electronic oil pump 4 directly supplies oil to the lubrication circuit 5.
It should be noted that, the vehicle gear-shifting demand signal may be identified by the TCU, and when the TCU identifies the gear-shifting demand, the rotational speed of the electronic oil pump 4 may be requested according to calibrated parameters, such as the pressure, the flow, and the like of the gear shift. When the vehicle gear-shifting demand signal is no gear-shifting demand, the flow provided by the electronic oil pump 4 only needs to meet the leakage of the flow of the whole control system and the flow demand of the lubrication system, the rotating speed of the electronic oil pump 4 can be requested according to the current gear of the vehicle, and the rotating speed of the electronic oil pump 4 can be determined according to the flow characteristic tables of the electronic oil pump 4 under different oil pressures.
It can be understood that the vehicle gear-shifting demand signal is obtained when the rotation speed of the engine is equal to 0, and when the gear-shifting demand signal of the vehicle is a gear-shifting demand, the electronic oil pump 4 is respectively supplied with oil to the control loop 6 and the lubrication loop 5 through the main oil way 11, and when the vehicle does not have the gear-shifting demand, the electronic oil pump 4 is directly supplied with oil to the lubrication loop 5, so that the gear-shifting demand is met, the oil consumption is reduced, and the fuel economy of the whole vehicle is improved.
Of course, it is only a preferable embodiment to relate the rotation speed of the electronic oil pump 4 to the shift signal of the vehicle, and it is also possible to relate the rotation speed of the electronic oil pump 4 to the clutch flow rate demand signal, and when the clutch flow rate demand signal indicates a flow rate demand, the electronic oil pump 4 is supplied with oil to the control circuit 6 and the lubrication circuit 5 through the main oil passage 11, respectively. When the clutch flow demand signal is no flow demand, the electronic oil pump 4 is directly supplied with oil to the lubrication circuit 5. In addition, the clutch flow demand signal in this embodiment may also be obtained by the TCU.
As a further preference, as shown in fig. 4, the lubrication circuit 5 in this embodiment comprises a first lubrication branch 51 for lubricating the bearings and gears, and a second lubrication branch 52 for lubricating the clutch 12. The control circuit 6 includes a clutch control branch 61, a shift control branch 62.
The oil outlet of the electronic oil pump 4 is connected in series with a first control valve element 7, the first control valve element 7 is provided with a working position for supplying oil to the main oil path 11 and a working position for supplying oil to the second control valve element 8, an oil cooler 501 and a filter press 502 which are sequentially arranged are connected in series in the lubrication circuit 5, and the second control valve element 8 is provided with a working position for supplying oil to the oil cooler 501 and a working position for directly supplying oil to the first lubrication branch 51 and the second lubrication branch 52.
The main oil path 11 is provided with a proportional pressure electromagnetic valve 9, the first lubrication branch 51 is provided with a first mechanical reversing valve 511, the first mechanical reversing valve 511 is controlled by the proportional pressure electromagnetic valve 9, and the gear shifting control branch 62 is connected with the main oil path 11 through the proportional pressure electromagnetic valve 9.
As shown in fig. 4, in the present embodiment, the first control valve element 7 is a two-position three-way solenoid valve, and the second control valve element 8 is a two-position three-way mechanical valve. The arrangement of the first control valve element 7 and the second control valve element 8 enables the electronic oil pump 4 to supply oil to the main oil path 11 or to supply oil to the lubrication circuit 5 alone, and if the oil pressure at the outlet of the electronic oil pump 4 is high, the electronic oil pump 4 can also supply oil to the first lubrication branch 51 and the second lubrication branch 52 directly, which is beneficial to ensuring the oil supply efficiency of the electronic oil pump 4.
And the gear-shifting control branch 62 is connected with the main oil way 11 through the proportional pressure electromagnetic valve 9, so that the flow and the pressure of the oil flowing into the gear-shifting control branch 62 from the main oil way 11 can be accurately and stably controlled, meanwhile, the first mechanical reversing valve 511 is controlled by the proportional pressure electromagnetic valve 9, the number of control valves is reduced, the cost is reduced, the number of control channels of a TCU (automatic gearbox control unit) of a vehicle is reduced, and the arrangement is convenient.
It should be noted that the lubrication circuit 5 in this embodiment includes both the first lubrication branch 51 for the bearing and the gear and the second lubrication branch 52 for lubricating the clutch 12 is only a preferred embodiment, and the lubrication circuit 5 includes only the first lubrication branch 51 or only the second lubrication branch 52. Likewise, the control circuit 6 may also include only the clutch control branch 61 or only the shift control branch 62. In addition, the bearings and gears lubricated by the first lubrication branch 51 described above, that is, the bearings and gears in the gear box 14 on the vehicle, and the first lubrication branch 51 may lubricate only the bearings or only the gears.
In the present embodiment, as a preferred embodiment, the shift control branch 62 includes a first shift control branch 621 and a second shift control branch 623, the first shift control branch 621 is provided with a first shift solenoid valve 622 connected to the proportional pressure solenoid valve 9, the first shift control branch 621 includes two shift units 625, and each shift unit 625 is connected to the first shift solenoid valve 622 through a second mechanical reversing valve 626. The second shift control branch 623 is provided with a second shift solenoid 624 connected to the proportional pressure solenoid 9. The main oil passage 11 is provided with an electromagnetic directional valve 10, and the second mechanical directional valve 626 and the second control valve 8 are controlled by the electromagnetic directional valve 10.
It will be appreciated that by providing the second mechanical directional valve 626 and having both the second mechanical directional valve 626 and the second control valve member 8 controlled by the electromagnetic directional valve 10, the number of solenoid valves can be reduced while increasing the number of gear steps, thereby simplifying the control system structure and reducing the cost thereof.
As shown in fig. 1, the proportional pressure solenoid valve 9 is a two-position three-way valve element having an operating position in which the main oil passage 11 is in communication with the shift control branch 62, and an operating position in which the shift control branch 62 is in communication with the transmission oil pan 1. The first shift solenoid valve 622 and the second shift solenoid valve 624 are three-position four-way proportional flow valves, and when the two valves are in the operating positions at both ends, the operating positions of the shift unit 625 can be switched, so that the gear of the transmission can be switched. When the shift solenoid valve is in the intermediate operating position, it is possible to maintain the shift unit 625 in a certain operating position.
It should be noted that the shifting unit 625 in this embodiment may be a shift control piston commonly used in the prior art. In addition, the first shift control branch 621 and the second shift control branch 623 described above can realize the shift of six forward gears or five forward gears and one reverse gear of the transmission. In the event that an increase in gear is desired, the shift control subcircuit may be correspondingly increased, or the number of shift units 625 within each shift control subcircuit may be increased.
It can be understood that the flow entering each gear shifting branch circuit can be controlled by arranging the gear shifting electromagnetic valve in each gear shifting branch circuit, so that the quick response of a gear shifting system is ensured, and the gear shifting smoothness is better.
In addition, the oil cooler 501 and the filter press 502 are disposed in the lubrication circuit 5, which can cool and filter the oil in the lubrication circuit 5, so as to remove impurities in the oil in the circuit, and facilitate better lubrication of the components to be lubricated.
In this example, a filter press bypass valve 503 is connected in parallel to both ends of a filter press 502, and an oil cooler bypass valve 504 is provided in the lubrication circuit 5 in parallel between an oil inlet end of the oil cooler 501 and an oil outlet end of the filter press 502. By providing the filter press bypass valve 503, after the filter press 502 is blocked seriously, the oil can enter each lubrication branch through the filter press bypass valve 503, so as to ensure enough oil to complete lubrication.
In addition, the oil cooler bypass valve 504 has two working positions of connection and disconnection, when the pressure in the oil path is not high, the oil cooler bypass valve 504 is in a disconnected state and does not work, when the oil pressure in the oil path at the front end of the oil cooler 501 is high, the oil in the lubricating loop 5 can enter the oil cooler bypass valve 504, the pressure in the oil path is relieved, the oil cooler 501 and the filter press 502 are protected, and damage to the oil cooler 501 and the filter press 502 caused by the too high oil pressure in the loop is avoided.
Furthermore, as a further preference, in the present embodiment a pressure limiting valve 505 is connected in the lubrication circuit 5, the pressure limiting valve 505 being connected to the oil inlet of the mechanical oil pump 3. As shown in fig. 1, the pressure limiting valve 505 has two states of connection and disconnection, when the oil pressure in the lubrication circuit 5 is high, the pressure limiting valve 505 can be in a connection state, and the lubrication circuit 5 is connected with the inlet of the mechanical oil pump 3, so that backflow of part of oil is realized, and the oil circuit is protected, and at the same time, the suction of the mechanical oil pump 3 at a high rotation speed can be prevented.
Of course, the present embodiment is provided with the pressure filter bypass valve 503, the oil cooler bypass valve 504, and the pressure limiting valve 505 as only one preferred embodiment, and one or two of the pressure filter bypass valve 503, the oil cooler bypass valve 504, and the pressure limiting valve 505 may be provided.
In the present embodiment, a throttle 512 is connected in parallel to both ends of the first mechanical directional valve 511. A second accumulator 16 is connected to the oil outlet end of the proportional pressure solenoid valve 9. As shown in fig. 1, the first mechanical reversing valve 511 is a two-position, two-way valve member having two operating positions on and off. By providing the throttle valve 512, an adjustment of the flow of the first lubrication branch 51 is facilitated.
Specifically, when the first lubrication branch 51 needs a large flow, the proportional pressure solenoid valve 9 controls the first mechanical reversing valve 511 to be in a communication working position, so that oil in the lubrication circuit 5 enters the gear box 14 through the first mechanical reversing valve 511. When the first lubrication branch 51 needs a small flow, the proportional pressure electromagnetic valve 9 controls the first mechanical reversing valve 511 to be in a disconnected working position, so that oil in the lubrication circuit 5 enters the gear box 14 through the throttle valve 512, and the adjustment of the oil amount entering the gear box 14 is realized.
It will be appreciated that by providing the second accumulator 16, it is advantageous to increase the stability of the oil pressure in the oil passage, avoiding pressure shocks in the oil passage. In the present embodiment, the second lubrication branch 52 is provided with a proportional flow solenoid valve 521, and the clutch control branch 61 is provided with clutch branches corresponding to the clutches 12 one by one, and each clutch branch is provided with a clutch pressure control solenoid valve 611.
As shown in fig. 4, the proportional flow solenoid valve 521 is a two-position, two-way proportional flow valve, and the oil that enters the second lubrication branch 52 lubricates the two clutches 12 in the clutch control branch 61 in sequence. The clutch pressure control solenoid valve 611 is a two-position three-way solenoid valve having a working position for supplying oil to the clutch 12 and a working position for allowing the oil in the clutch 12 to flow back into the transmission oil pan 1, and the oil entering each clutch branch passage passes through each clutch pressure control solenoid valve 611 to enter each clutch 12.
It will be appreciated that by providing proportional flow solenoid valve 521, a linear adjustment of the lubrication flow into second lubrication branch 52 is facilitated. The clutch pressure control solenoid valve 611 is provided on each clutch branch, so that the on-off of each clutch branch can be controlled, and the coupling and the decoupling of the clutch 12 can be controlled.
Of course, the present embodiment is provided with both the throttle valve 512 and the proportional flow solenoid valve 521 and the clutch pressure control solenoid valve 611, and one or two of the throttle valve 512, the proportional flow solenoid valve 521, and the clutch pressure control solenoid valve 611 may be provided as a preferred embodiment.
As a further preferred embodiment, a third accumulator 613 and an oil pressure sensor 612 are connected to the oil outlet of the clutch pressure control solenoid valve 611. By providing the oil pressure sensor 612, the oil pressure in each clutch branch can be monitored in real time, so that the oil pressure in the branch can be adjusted in time. The third accumulator 613 is provided to keep the pressure of each clutch 12 stable.
In addition, in the present embodiment, the main oil passage 11 is provided with a third control valve element 17, and the third control valve element 17 has a working position for shutting off the oil supply to the lubrication circuit 5, a working position for supplying oil to the lubrication circuit 5, and a working position for supplying oil to the lubrication circuit 5 and returning part of the lubricating oil to the oil inlet of the mechanical oil pump 3. As shown in fig. 4, the third control valve 17 is a three-position four-way pressure regulating valve, and it can be understood that by providing the third control valve 17 with the above-mentioned working position, it is possible to control the main oil path 11 to supply oil to the lubrication circuit 5, and at the same time, it is also possible to make part of the oil flow back to the oil inlet of the mechanical oil pump 3, so as to further avoid the suction of air at high rotation speed of the mechanical oil pump 3.
As a preferred embodiment, in this example, the third control valve member 17 is controlled by the main pressure regulating solenoid valve 13, and the outlet of the main pressure regulating solenoid valve 13 is connected to the first accumulator 15. In particular, as shown in fig. 4, the main regulator solenoid valve 13 is a two-position three-way solenoid valve having an operating position in which the main oil passage 11 communicates with one of the control ports of the third control valve element 17, and an operating position in which one of the control ports of the third control valve element 17 communicates with the transmission oil pan 1. And the main pressure regulating solenoid valve 13 is connected in parallel between the two control ports of the third control valve member 17 to realize the adjustment of the working position of the third control valve member 17. The first accumulator 15 is able to stabilize the pressure of the main regulator solenoid valve 13, facilitating its regulation of the third control valve member 17.
In use of the electro-hydraulic control system of the present embodiment, as shown in fig. 4, both the electronic oil pump 4 and the mechanical oil pump 3 communicate with the transmission oil pan 1 to pump oil within the oil pan into the oil passage. In order to remove impurities in the oil, a suction filter 2 is installed in the oil pan 1 of the gearbox, and the oil in the oil pan 1 of the gearbox can be filtered for the first time.
In addition, in order to ensure that the oil in the oil way has enough pressure and can reduce the torque loss of the gearbox, preferably, the electronic oil pump 4 of the embodiment adopts a high-pressure small-flow electronic oil pump 4, and the mechanical oil pump 3 can adopt a small-displacement vane pump so as to ensure that the oil pressure in the oil way is enough, reduce the torque loss and improve the efficiency of the gearbox and the fuel economy of the whole vehicle.
It should be noted that, in this embodiment, the electronic oil pump 4 is a high-pressure small-flow electronic oil pump 4, the mechanical oil pump 3 is a small-displacement vane pump, which is just a preferred embodiment, and in actual design, the electronic oil pump 4 and the mechanical oil pump 3 may be selected according to specific working requirements. As also shown in fig. 4, in order to prevent the return of the system, a check valve is installed at the outlet of the mechanical oil pump 3, and the oil pumped by the mechanical oil pump 3 passes through the check valve, enters the main oil path 11, and meets the oil pumped by the electronic oil pump 4.
The oil entering the main oil passage 11, a part of which enters the control circuit 6, and another part of which enters the third control valve element 17, and enters the lubrication circuit 5 through the third control valve element 17. The oil entering the control circuit 6 may flow into the shift control branch 62 and the clutch control branch 61 as desired. The oil entering the lubrication circuit 5 can flow into the first lubrication branch 51 and the second lubrication branch 52 according to the requirement.
When the gearbox electrohydraulic control system works, if the engine rotating speed signal is larger than 0, and the flow rate of the mechanical oil pump 3 is larger than the flow rate requirement of the control circuit and smaller than the flow rate requirement of the lubrication circuit 5, the flow route of oil in the system is shown in fig. 5. And the electronic oil pump 4 directly supplies oil into the first lubrication branch 51 and the second lubrication branch 52, the flow route of the oil is shown in fig. 6.
When the engine speed signal is greater than 0 and the flow rate of the mechanical oil pump 3 is greater than the flow rate demand of the lubrication circuit 5, the flow path of the oil in the system is as shown in fig. 7. In addition, the mechanical oil pump 3 provides more oil, and a flow path of part of the oil flowing back to the oil inlet of the mechanical oil pump 3 is shown in fig. 8. When the engine speed signal is greater than 0 and the mechanical oil pump 3 flow is less than the control loop flow demand, the system internal oil flow path is as shown in fig. 9. In addition, the flow path of the oil when the engine speed signal is equal to 0 and the vehicle shift demand signal is a shift demand is shown in fig. 10. The oil flow path is shown in FIG. 11 when the engine speed signal is equal to 0 and the vehicle shift demand signal is no shift demand.
According to the control method of the gearbox electrohydraulic control system, the electronic oil pump 4 supplies oil to the control system according to the flow requirement of the control circuit and the flow requirement of the lubrication circuit, so that the whole oil supply efficiency is improved, the electronic oil pump 4 directly supplies oil to the lubrication circuit 5, the electronic oil pump 4 can provide enough cooling and lubrication flow conveniently, and the whole oil supply efficiency is further improved. And when the current flow of the electronic oil pump 4 is not lower than a preset flow threshold, oil can be directly supplied to each lubrication branch, so that the pressure at the oil outlet of the electronic oil pump 4 is reduced, and the oil supply efficiency is improved.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, alternatives, and improvements that fall within the spirit and scope of the invention.
Claims (9)
1. A control method of an electrohydraulic control system of a gearbox is characterized by comprising the following steps of:
The electro-hydraulic control system of the gearbox is provided with a mechanical oil pump (3) and an electronic oil pump (4), a main oil way (11), a control loop (6) and a lubrication loop (5) which are connected with the main oil way (11), wherein the lubrication loop (5) comprises a plurality of lubrication branches;
the control method comprises the following steps:
Acquiring an engine rotating speed signal;
When the engine speed signal is greater than 0, acquiring a control loop flow demand and a lubrication loop flow demand;
When the flow rate of the mechanical oil pump (3) is larger than the flow rate requirement of the control loop and smaller than the flow rate requirement of the lubrication loop, the mechanical oil pump (3) and the electronic oil pump (4) work together, and the electronic oil pump (4) directly supplies oil to the lubrication loop (5);
acquiring a vehicle gear shifting demand signal or a clutch flow demand signal when the engine speed signal is equal to 0;
when the vehicle gear-shifting demand signal is a gear-shifting demand signal or the clutch flow demand signal is a flow demand signal, the electronic oil pump (4) supplies oil to the control loop (6) and the lubrication loop (5) through the main oil way (11) respectively;
When the vehicle gear-shifting demand signal is no gear-shifting demand or the clutch flow demand signal is no flow demand, the electronic oil pump (4) directly supplies oil to the lubrication circuit (5).
2. A control method of an electro-hydraulic control system of a transmission according to claim 1, further comprising:
when the engine speed signal is greater than 0, acquiring the flow demand of the lubrication circuit;
When the flow rate of the mechanical oil pump (3) is greater than the flow rate requirement of the lubrication circuit, only the mechanical oil pump (3) works, and the mechanical oil pump (3) supplies oil to the control circuit (6) and the lubrication circuit (5) through the main oil circuit (11) respectively.
3. A control method of an electro-hydraulic control system of a transmission according to claim 1, further comprising:
When the engine speed signal is greater than 0, acquiring a control loop flow demand;
When the flow rate of the mechanical oil pump (3) is smaller than the flow rate requirement of the control loop, the mechanical oil pump (3) and the electronic oil pump (4) work together, and the electronic oil pump (4) supplies oil to the main oil way (11).
4. A control method of an electro-hydraulic control system of a transmission according to claim 1, further comprising:
when the electronic oil pump (4) directly supplies oil to the lubrication circuit (5), acquiring the current flow of the electronic oil pump (4);
When the current flow is not lower than a preset flow threshold, the electronic oil pump (4) directly supplies oil to each lubrication branch;
when the current flow rate is lower than the preset flow rate threshold value, the electronic oil pump (4) supplies oil to each lubricating branch through an oil cooler (501) and/or a pressure filter (502).
5. A control method of a transmission electro-hydraulic control system according to any one of claims 1 to 4, characterized in that:
The lubrication circuit (5) comprises at least one of a first lubrication branch (51) for lubricating the bearing and/or the gear, and a second lubrication branch (52) for lubricating the clutch (12);
The control circuit (6) comprises at least one of a clutch control branch (61) and a gear shift control branch (62).
6. A control method of an electro-hydraulic control system for a transmission according to claim 5, wherein:
The oil outlet of the electronic oil pump (4) is connected with a first control valve element (7) in series, the first control valve element (7) is provided with a working position for supplying oil to the main oil way (11) and a working position for supplying oil to a second control valve element (8), the lubricating circuit (5) is connected with an oil cooler (501) and a filter press (502) which are sequentially arranged in series, and the second control valve element (8) is provided with a working position for supplying oil to the oil cooler (501) and a working position for directly supplying oil to the first lubricating branch (51) and the second lubricating branch (52);
Be equipped with proportion pressure solenoid valve (9) on main oil circuit (11), be equipped with first mechanical switching-over valve (511) on first lubrication branch road (51), first mechanical switching-over valve (511) by proportion pressure solenoid valve (9) control, shift control branch road (62) pass through proportion pressure solenoid valve (9) with main oil circuit (11) are connected.
7. A control method of an electro-hydraulic control system of a transmission according to claim 6, wherein:
The gear shifting control branch circuit (62) at least comprises a first gear shifting control branch circuit (621) and a second gear shifting control branch circuit (623), a first gear shifting electromagnetic valve (622) connected with the proportional pressure electromagnetic valve (9) is arranged on the first gear shifting control branch circuit (621), the first gear shifting control branch circuit (621) comprises a plurality of gear shifting units (625), and each gear shifting unit (625) is connected with the first gear shifting electromagnetic valve (622) through a second mechanical reversing valve (626);
The second gear shifting control branch (623) is provided with a second gear shifting electromagnetic valve (624) connected with the proportional pressure electromagnetic valve (9);
an electromagnetic directional valve (10) is arranged on the main oil way (11), and the second mechanical directional valve (626) and the second control valve (8) are controlled by the electromagnetic directional valve (10).
8. A control method of an electro-hydraulic control system of a transmission according to claim 6, wherein:
the two ends of the pressure filter (502) are connected with a pressure filter bypass valve (503) in parallel; and/or the number of the groups of groups,
An oil cooler bypass valve (504) connected in parallel between the oil inlet end of the oil cooler (501) and the oil outlet end of the pressure filter (502) is arranged in the lubricating loop (5); and/or the number of the groups of groups,
A pressure limiting valve (505) is connected in the lubrication circuit (5), and the pressure limiting valve (505) is connected to an oil inlet of the mechanical oil pump (3).
9. A control method of an electro-hydraulic control system for a transmission according to claim 5, wherein:
A third control valve element (17) is arranged in the main oil way (11), the third control valve element (17) is provided with a working position for cutting off the oil supply to the lubrication circuit (5), a working position for supplying oil to the lubrication circuit (5) and making part of the lubricating oil flow back to an oil inlet of the mechanical oil pump (3);
the third control valve element (17) is controlled by a main pressure regulating electromagnetic valve (13), and an outlet of the main pressure regulating electromagnetic valve (13) is connected with a first energy accumulator (15).
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